80 FR 69277 - Energy Conservation Program: Test Procedures for Central Air Conditioners and Heat Pumps
DEPARTMENT OF ENERGY
Federal Register Volume 80, Issue 216 (November 9, 2015)
Page Range
69277-69456
FR Document
2015-23439
The U.S. Department of Energy (DOE) proposes to revise its test procedures for central air conditioners and heat pumps established under the Energy Policy and Conservation Act. DOE proposed amendments to the test procedure in a June 2010 notice of proposed rulemaking (NOPR), an April 2011 supplemental notice of proposed rulemaking (SNOPR), and an October 2011 SNOPR. DOE provided additional time for stakeholder comment in a December 2011 extension of the comment period for the October 2011 SNOPR. DOE received further public comment for revising the test procedure in a November 2014 Request for Information for energy conservation standards for central air conditioners and heat pumps. DOE proposes in this SNOPR: A new basic model definition as it pertains to central air conditioners and heat pumps and revised rating requirements; revised alternative efficiency determination methods; termination of active waivers and interim waivers; revised procedures to determine off mode power consumption; changes to the test procedure that would improve test repeatability and reduce test burden; clarifications to ambiguous sections of the test procedure intended also to improve test repeatability; inclusion of, amendments to, and withdrawals of test procedure revisions proposed in published test procedure notices in the rulemaking effort leading to this supplemental notice of proposed rulemaking; and changes to the test procedure that would improve field representativeness. Some of these proposals also include incorporation by reference of updated industry standards. DOE welcomes comments from the public on any subject within the scope of this test procedure rulemaking.
Federal Register, Volume 80 Issue 216 (Monday, November 9, 2015)
[Federal Register Volume 80, Number 216 (Monday, November 9, 2015)]
[Proposed Rules]
[Pages 69277-69456]
From the Federal Register Online [www.thefederalregister.org]
[FR Doc No: 2015-23439]
[[Page 69277]]
Vol. 80
Monday,
No. 216
November 9, 2015
Part II
Department of Energy
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10 CFR Parts 429 and 430
Energy Conservation Program: Test Procedures for Central Air
Conditioners and Heat Pumps; Proposed Rule
Federal Register / Vol. 80 , No. 216 / Monday, November 9, 2015 /
Proposed Rules
[[Page 69278]]
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DEPARTMENT OF ENERGY
10 CFR Parts 429 and 430
[Docket No. EERE-2009-BT-TP-0004]
RIN 1904-AB94
Energy Conservation Program: Test Procedures for Central Air
Conditioners and Heat Pumps
AGENCY: Office of Energy Efficiency and Renewable Energy, Department of
Energy.
ACTION: Supplemental notice of proposed rulemaking.
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SUMMARY: The U.S. Department of Energy (DOE) proposes to revise its
test procedures for central air conditioners and heat pumps established
under the Energy Policy and Conservation Act. DOE proposed amendments
to the test procedure in a June 2010 notice of proposed rulemaking
(NOPR), an April 2011 supplemental notice of proposed rulemaking
(SNOPR), and an October 2011 SNOPR. DOE provided additional time for
stakeholder comment in a December 2011 extension of the comment period
for the October 2011 SNOPR. DOE received further public comment for
revising the test procedure in a November 2014 Request for Information
for energy conservation standards for central air conditioners and heat
pumps. DOE proposes in this SNOPR: A new basic model definition as it
pertains to central air conditioners and heat pumps and revised rating
requirements; revised alternative efficiency determination methods;
termination of active waivers and interim waivers; revised procedures
to determine off mode power consumption; changes to the test procedure
that would improve test repeatability and reduce test burden;
clarifications to ambiguous sections of the test procedure intended
also to improve test repeatability; inclusion of, amendments to, and
withdrawals of test procedure revisions proposed in published test
procedure notices in the rulemaking effort leading to this supplemental
notice of proposed rulemaking; and changes to the test procedure that
would improve field representativeness. Some of these proposals also
include incorporation by reference of updated industry standards. DOE
welcomes comments from the public on any subject within the scope of
this test procedure rulemaking.
DATES: DOE will accept comments, data, and information regarding this
supplemental notice of proposed rulemaking (SNOPR) no later than
December 9, 2015. See section V, ``Public Participation,'' for details.
ADDRESSES: Any comments submitted must identify the SNOPR for test
procedures for central air conditioners and heat pumps, and provide
docket number EE-2009-BT-TP-0004 and/or regulatory information number
(RIN) number 1904-AB94. Comments may be submitted using any of the
following methods:
1. Federal eRulemaking Portal: www.regulations.gov. Follow the
instructions for submitting comments.
2. Email: [email protected]. Include the docket
number EE-2009-BT-TP-0004 and/or 1904-AB94 RIN in the subject line of
the message.
3. Mail: Ms. Brenda Edwards, U.S. Department of Energy, Building
Technologies Office, Mailstop EE-2J, 1000 Independence Avenue SW.,
Washington, DC 20585-0121. If possible, please submit all items on a
CD, in which case it is not necessary to include printed copies.
4. Hand Delivery/Courier: Ms. Brenda Edwards, U.S. Department of
Energy, Building Technologies Office, 950 L'Enfant Plaza SW., Suite
600, Washington, DC 20024.
Telephone: (202) 586-2945. If possible, please submit all items on
a CD, in which case it is not necessary to include printed copies.
For detailed instructions on submitting comments and additional
information on the rulemaking process, see section V of this document
(Public Participation).
Docket: The docket, which includes Federal Register notices, public
meeting attendee lists and transcripts, comments, and other supporting
documents/materials, is available for review at www.regulations.gov.
All documents in the docket are listed in the regulations.gov index.
However, some documents listed in the index, such as those containing
information that is exempt from public disclosure, may not be publicly
available.
A link to the docket Web page can be found at:
www1.eere.energy.gov/buildings/appliance_standards/rulemaking.aspx/ruleid/72. This Web page will contain a link to the docket for this
notice on the www.regulations.gov site. The www.regulations.gov Web
page will contain simple instructions on how to access all documents,
including public comments, in the docket. See section V for information
on how to submit comments through regulations.gov.
FOR FURTHER INFORMATION CONTACT:
Ashley Armstrong, U.S. Department of Energy, Office of Energy
Efficiency and Renewable Energy, Building Technologies Program, EE-2J,
1000 Independence Avenue SW., Washington, DC 20585-0121. Telephone:
(202) 586-6590. Email: [email protected].
Johanna Hariharan, U.S. Department of Energy, Office of the General
Counsel, GC-33, 1000 Independence Avenue SW., Washington, DC, 20585-
0121. Telephone: (202) 287-6307. Email: [email protected].
For further information on how to submit a comment, review other
public comments and the docket, or participate in the public meeting,
contact Ms. Brenda Edwards at (202) 586-2945 or by email:
[email protected].
SUPPLEMENTARY INFORMATION: DOE intends to incorporate by reference the
following industry standards into Part 430:
(1) ANSI/AHRI 210/240-2008 with Addenda 1 and 2: Performance Rating
of Unitary Air-Conditioning & Air-Source Heat Pump Equipment, 2012;
(2) AHRI 210/240-Draft: Performance Rating of Unitary Air-
Conditioning & Air-Source Heat Pump Equipment;
(3) ANSI/AHRI 1230-2010 with Addendum 2: Performance Rating of
Variable Refrigerant Flow (VRF) Multi-Split Air-Conditioning and Heat
Pump Equipment, 2010;
(4) ASHRAE 23.1-2010: Methods of Testing for Rating the Performance
of Positive Displacement Refrigerant Compressors and Condensing Units
that Operate at Subcritical Temperatures of the Refrigerant;
(5) ASHRAE Standard 37-2009, Methods of Testing for Rating
Electrically Driven Unitary Air-Conditioning and Heat Pump Equipment;
(6) ASHRAE 41.1-2013: Standard Method for Temperature Measurement;
ASHRAE 41.6-2014: Standard Method for Humidity Measurement;
(7) ASHRAE 41.9-2011: Standard Methods for Volatile-Refrigerant
Mass Flow Measurements Using Calorimeters;
(8) ASHRAE/AMCA 51-07/210-07, Laboratory Methods of Testing Fans
for Certified Aerodynamic Performance Rating.
Copies of ANSI/AHRI 210/240-2008 and ANSI/AHRI 1230-2010 can be
obtained from the Air-Conditioning, Heating, and Refrigeration
Institute, 2111 Wilson Boulevard, Suite 500, Arlington, VA 22201, USA,
703-524-8800, or by going to http://www.ahrinet.org/site/686/Standards/HVACR-Industry-Standards/Search-Standards. A copy of AHRI 210/240-
[[Page 69279]]
Draft is available on the rulemaking Web page (Docket EERE-2009-BT-TP-
0004-0045).
Copies of ASHRAE 23.1-2010, ASHRAE Standard 37-2009, ASHRAE 41.1-
2013, and ASHRAE 41.9-2011 can be purchased from ASHRAE's Web site at
https://www.ashrae.org/resources-publications.
Copies of ASHRAE/AMCA 51-07/210-07 can be purchases from AMCA's Web
site at http://www.amca.org/store/index.php.
Table of Contents
I. Authority and Background
A. Authority
B. Background
II. Summary of the Supplementary Notice of Proposed Rulemaking
III. Discussion
A. Definitions, Testing, Rating, and Compliance of Basic Models
of Central Air Conditioners and Heat Pumps
1. Basic Model Definition
2. Additional Definitions
3. Determination of Certified Rating
4. Compliance With Federal (National or Regional) Standards
5. Certification Reports
6. Represented Values
7. Product-Specific Enforcement Provisions
B. Alternative Efficiency Determination Methods
1. General Background
2. Terminology
3. Elimination of the Pre-Approval Requirement
4. AEDM Validation
5. Requirements for Independent Coil Manufacturers
6. AEDM Verification Testing
7. Failure to Meet Certified Ratings
8. Action Following a Determination of Noncompliance
C. Waiver Procedures
1. Termination of Waivers Pertaining to Air-to-Water Heat Pump
Products With Integrated Domestic Water Heating
2. Termination of Waivers Pertaining to Multi-Circuit Products
3. Termination of Waiver and Clarification of the Test Procedure
Pertaining to Multi-Blower Products
4. Termination of Waiver Pertaining to Triple-Capacity, Northern
Heat Pump Products
D. Measurement of Off Mode Power Consumption
1. Test Temperatures
2. Calculation and Weighting of P1 and P2
3. Products With Large, Multiple or Modulated Compressors
4. Procedure for Measuring Low-Voltage Component Power
5. Revision of Off-Mode Power Consumption Equations
6. Off-Mode Power Consumption for Split Systems
7. Time Delay Credit
8. Test Metric for Off-Mode Power Consumption
9. Impacts on Product Reliability
10. Representative Measurement of Energy Use
E. Test Repeatability Improvement and Test Burden Reduction
1. Indoor Fan Speed Settings
2. Requirements for the Refrigerant Lines and Mass Flow Meter
3. Outdoor Room Temperature Variation
4. Method of Measuring Inlet Air Temperature on the Outdoor Side
5. Requirements for the Air Sampling Device
6. Variation in Maximum Compressor Speed With Outdoor
Temperature
7. Refrigerant Charging Requirements
8. Alternative Arrangement for Thermal Loss Prevention for
Cyclic Tests
9. Test Unit Voltage Supply
10. Coefficient of Cyclic Degradation
11. Break-in Periods Prior to Testing
12. Industry Standards That Are Incorporated by Reference
13. Withdrawing References to ASHRAE Standard 116-1995 (RA 2005)
14. Additional Changes Based on AHRI 210/240-Draft
15. Damping Pressure Transducer Signals
F. Clarification of Test Procedure Provisions
1. Manufacturer Consultation
2. Incorporation by Reference of ANSI/AHRI Standard 1230-2010
3. Replacement of the Informative Guidance Table for Using the
Federal Test Procedure
4. Clarifying the Definition of a Mini-Split System
5. Clarifying the Definition of a Multi-Split System
G. Test Procedure Reprint
H. Improving Field Representativeness of the Test Procedure
1. Minimum External Static Pressure Requirements for
Conventional Central Air Conditioners and Heat Pumps
2. Minimum External Static Pressure Adjustment for Blower Coil
Systems Tested With Condensing Furnaces
3. Default Fan Power for Coil-Only Systems
4. Revised Heating Load Line
5. Revised Heating Mode Test Procedure for Products Equipped
With Variable-Speed Compressors
I. Identified Test Procedure Issues DOE May Consider in Future
Rulemakings
1. Controlling Variable Capacity Units to Field Conditions
2. Revised Ambient Test Conditions
3. Performance Reporting at Certain Air Volume Flow Rates
4. Cyclic Test With a Wet Coil
5. Inclusion of the Calculation for Sensible Heating Ratio
J. Compliance With Other Energy Policy and Conservation Act
Requirements
1. Test Burden
2. Potential Incorporation of International Electrotechnical
Commission Standard 62301 and International Electrotechnical
Commission Standard 62087
IV. Procedural Issues and Regulatory Review
A. Review Under Executive Order 12866
B. Review Under the Regulatory Flexibility Act
C. Review Under the Paperwork Reduction Act of 1995
D. Review Under the National Environmental Policy Act of 1969
E. Review Under Executive Order 13132
F. Review Under Executive Order 12988
G. Review Under the Unfunded Mandates Reform Act of 1995
H. Review Under the Treasury and General Government
Appropriations Act, 1999
I. Review Under Executive Order 12630
J. Review Under the Treasury and General Government
Appropriations Act, 2001
K. Review Under Executive Order 13211
L. Review Under Section 32 of the Federal Energy Administration
Act of 1974
M. Description of Materials Incorporated by Reference
V. Public Participation
A. Attendance at Public Meeting
B. Procedure for Submitting Prepared General Statements for
Distribution
C. Conduct of Public Meeting
D. Submission of Comments
E. Issues on Which DOE Seeks Comment
VI. Approval of the Office of the Secretary
I. Authority and Background
A. Authority
Title III, Part B of the Energy Policy and Conservation Act of 1975
(EPCA or the Act), Pub. L. 94-163 (42 U.S.C. 6291-6309, as codified),
established the Energy Conservation Program for Consumer Products Other
Than Automobiles, a program covering most major household appliances,
including the single phase central air conditioners and heat pumps \1\
with rated cooling capacities less than 65,000 British thermal units
per hour (Btu/h) that are the focus of this notice.\2\ (42 U.S.C.
6291(1)-(2), (21) and 6292(a)(3))
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\1\ Where this notice uses the terms ``HVAC'' or ``CAC/CHP'',
they are in reference specifically to central air conditioners and
heat pumps as covered by EPCA.
\2\ For editorial reasons, upon codification in the U.S. Code,
Part B was re-designated Part A.
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Under EPCA, the program consists of four activities: (1) Testing;
(2) labeling; (3) Federal energy conservation standards; and (4)
certification, compliance, and enforcement. The testing requirements
consist of test procedures that manufacturers of covered products must
use as the basis for certifying to DOE that their products comply with
applicable energy conservation standards adopted pursuant to EPCA and
for representing the efficiency of those products. (42 U.S.C. 6293(c);
42 U.S.C. 6295(s)) Similarly, DOE must use these test procedures in any
enforcement action to determine whether covered products comply with
these energy conservation standards. (42 U.S.C. 6295(s)) Under 42
U.S.C. 6293, EPCA sets forth criteria and procedures for DOE's adoption
and amendment of such test procedures. Specifically, EPCA provides that
an amended test procedure shall produce results which measure the
energy
[[Page 69280]]
efficiency, energy use, or estimated annual operating cost of a covered
product over an average or representative period of use, and shall not
be unduly burdensome to conduct. (42 U.S.C. 6293(b)(3)) In addition, if
DOE determines that a test procedure amendment is warranted, it must
publish proposed test procedures and offer the public an opportunity to
present oral and written comments on them. (42 U.S.C. 6293(b)(2))
Furthermore, DOE must review test procedures at least once every 7
years. (42 U.S.C 6293(b)(1)(A)) DOE last published a test procedure
final rule for central air conditioner and heat pumps on October 22,
2007. 72 FR 59906. Finally, in any rulemaking to amend a test
procedure, DOE must determine whether and the extent to which the
proposed test procedure would change the measured efficiency of a
system that was tested under the existing test procedure. (42 U.S.C.
6293(e)(1)) If DOE determines that the amended test procedure would
alter the measured efficiency of a covered product, DOE must amend the
applicable energy conservation standard accordingly. (42 U.S.C.
6293(e)(2))
DOE's existing test procedures for central air conditioners and
heat pumps adopted pursuant to these provisions appear under Title 10
of the Code of Federal Regulations (CFR) Part 430, Subpart B, Appendix
M (``Uniform Test Method for Measuring the Energy Consumption of
Central Air Conditioners and Heat Pumps''). These procedures establish
the currently permitted means for determining energy efficiency and
annual energy consumption of these products. Some amendments proposed
in this SNOPR will not alter the measured efficiency of central air
conditioners and heat pumps, and thus are being proposed as revisions
to the current Appendix M. Other amendments proposed in this SNOPR will
alter the measured efficiency, as represented in the regulating metrics
of energy efficiency ratio (EER), seasonal energy efficiency ratio
(SEER), and heating seasonal performance factor (HSPF). These
amendments are proposed as part of a new Appendix M1. The test
procedure changes proposed in this notice as part of a new Appendix M1,
if adopted, would not become mandatory until the existing energy
conservation standards are revised. (42 U.S.C. 6293(e)(2)) In revising
the energy conservation standards, DOE would create a cross-walk from
the existing standards under the current test procedure to what the
standards would be if tested using the revised test procedure. DOE
would then use the cross-walked equivalent of the existing standard as
the baseline for its standards analysis to prevent back-sliding as
required under 42 U.S.C. 6295(o)(1).
On December 19, 2007, the President signed the Energy Independence
and Security Act of 2007 (EISA 2007), Pub. L. 110-140, which contains
numerous amendments to EPCA. Section 310 of EISA 2007 established that
the Department's test procedures for all covered products must account
for standby mode and off mode energy consumption. (42 U.S.C.
6295(gg)(2)(A)) For central air conditioners and heat pumps, standby
mode is incorporated into the SEER metric, while off mode power
consumption is separately regulated. This SNOPR includes proposals
relevant to the determination of both SEER (including standby mode) and
off mode power consumption.
10 CFR 430.27 allows manufacturers to submit an application for an
interim waiver and/r a petition for a waiver granting relief from
adhering to the test procedure requirements found under 10 CFR part
430, subpart B, Appendix M. For those waivers that are active, however,
10 CFR 430.27(l) requires DOE to amend its regulations so as to
eliminate any need for the continuation of such waivers. To this end,
this notice proposes relevant amendments to its test procedure
concerning such waivers.
B. Background
This SNOPR addresses proposals and comments from three separate
rulemakings, two guidance documents, and a working group: (1) Proposals
for off mode test procedures made in earlier notices as part of this
rulemaking (Docket No. EERE-2009-BT-TP-0004); (2) proposals regarding
alternative efficiency determination methods (Docket No. EERE-2011-BT-
TP-0024); (3) stakeholder comments from a request for information
regarding energy conservation standards (Docket No. EERE-2014-BT-STD-
0048); (4) a draft guidance document related to testing and rating
split systems with blower coil units (Docket No. EERE-2014-BT-GUID-
0033); (5) a draft guidance document that deals with selecting units
for testing, rating, and certifying split-system combinations,
including discussion of basic models and of condensing units and
evaporator coils sold separately for replacement installation (Docket
No. EERE-2014-BT-GUID-0032); and (6) the recommendations of the
regional standards enforcement Working Group (Docket No. EERE-2011-BT-
CE-0077).
DOE's initial proposals for estimating off mode power consumption
in the test procedure for central air conditioners and heat pumps were
shared with the public in a notice of proposed rulemaking published in
the Federal Register on June 2, 2010 (June 2010 NOPR; 75 FR 31224) and
at a public meeting at DOE headquarters in Washington, DC on June 11,
2010. Subsequently, DOE published a supplemental notice of proposed
rulemaking (SNOPR) on April 1, 2011, in response to comments received
on the June 2010 NOPR and due to the results of additional laboratory
testing conducted by DOE. (April 2011 SNOPR) 76 FR 18105, 18127. DOE
received additional comments in response to the April 2011 SNOPR and
proposed an amended version of the off mode procedure that addressed
those comments in a second SNOPR on October 24, 2011 (October 2011
SNOPR). 76 FR 65616. DOE received additional comments during the
comment period of the October 24, 2011 SNOPR and the subsequent
extended comment period. 76 FR 79135.
Between the April 2011 and October 2011 SNOPRs, DOE published a
direct final rule (DFR) in the Federal Register on June 27, 2011 that
set forth amended energy conservation standards for central air
conditioners and central air conditioning heat pumps, including a new
standard for off mode electrical power consumption. (June 2011 DFR) 76
FR 37408. Units manufactured on or after January 1, 2015, are subject
to that standard for off mode electrical power consumption. 10 CFR
430.32(c)(6). However, on July 8, 2014, DOE published an enforcement
policy statement regarding off mode standards for central air
conditioners and central air conditioning heat pumps \3\ (July 2014
Enforcement Policy Statement) specifying that DOE will not assert civil
penalty authority for violation of the off mode standard until 180 days
following publication of a final rule establishing a test method for
measuring off mode electrical power consumption.
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\3\ Available at: http://energy.gov/sites/prod/files/2014/07/f17/Enforcement%20Policy%20Statement%20-%20cac%20off%20mode.pdf
(Last accessed March 30, 2015.)
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DOE also pursued, in a request for information (RFI) published on
April 18, 2011 (AEDM RFI) (76 FR 21673), and a NOPR published on May
31, 2012 (AEDM NOPR) (77 FR 32038), revisions to its existing
alternative efficiency determination methods (AEDM) and alternative
rating methods (ARM) requirements to improve the approach by which
manufacturers may use
[[Page 69281]]
modeling techniques as the basis to certify consumer products and
commercial and industrial equipment covered under EPCA. DOE also
published a final rule regarding AEDM requirements for commercial and
industrial equipment only (Commercial Equipment AEDM FR). 78 FR 79579.
This SNOPR addresses the proposals made and comments received in the
AEDM NOPR applicable to central air conditioners and heat pumps and
makes additional proposals.
On June 13, 2014, DOE published a notice of intent to form a
working group to negotiate enforcement of regional standards for
central air conditioners and requested nominations from parties
interested in serving as members of the Working Group. 79 FR 33870. On
July 16, 2014, the Department published a notice of membership
announcing the eighteen nominations that were selected to serve as
members of the Working Group, in addition to two members from Appliance
Standards and Rulemaking Federal Advisory Committee (ASRAC), and one
DOE representative. 79 FR 41456. The Working Group identified a number
of issues related to testing and certification that are being addressed
in this rule. In addition, all nongovernmental participants of the
Working Group approved the final report contingent on upon the issuance
of the final guidance on Docket No. EERE-2014-BT-GUID-0032 0032 and
Docket No. EERE-2014-BT-GUID-0033 consistent with the understanding of
the Working Group as set forth in its recommendations. (Docket No.
EERE-2011-BT-CE-0077-0070, Attachment) This SNOPR responds to comments
on the August 19 and 20, 2014, guidance documents related to testing
and rating split systems, which are discussed in more detail in section
III.A. The proposed changes supplant these two draft guidance
documents; DOE will not finalize the draft guidance documents and
instead will provide any necessary clarity through this notice and the
final rule. DOE believes the proposed changes are consistent with the
intent of the Working Group.
On November 5, 2014, DOE published a request for information for
energy conservation standards (ECS) for central air conditioners and
heat pumps (November 2014 ECS RFI). 79 FR 65603. In response, several
stakeholders provided comments suggesting that DOE amend the current
test procedure. This SNOPR responds to those test procedure-related
comments.
II. Summary of the Supplementary Notice of Proposed Rulemaking
This supplementary notice of proposed rulemaking (SNOPR) proposes
revising the certification requirements and test procedure for central
air conditioners and heat pumps based on various published material as
discussed in section I.B.
DOE proposes to revise the basic model definition, add additional
definitions for clarity, make certain revisions to the testing
requirements for determination of certified ratings, add certain
certification reporting requirements, revise requirements for
determination of represented values, and add product-specific
enforcement provisions. Some of the proposed revisions to the
certification requirements would impact the energy conservation
standard and thus would not be effective until the compliance date of
any amended energy conservation standards.
DOE proposes to update requirements for Alternative Rating Methods
(ARMs) used to determine performance metrics for central air
conditioners and heat pumps based on the regulations for Alternative
Efficiency Determination Methods (AEDMs) that are used to estimate
performance for commercial HVAC equipment. Specifically, for central
air conditioners and heat pumps, DOE proposes: (1) Revisions to
nomenclature regarding ARMs; (2) rescinding DOE pre-approval of an ARM
prior to use; (3) AEDM validation requirements; (4) a verification
testing process; (5) actions a manufacturer could take following a
verification test failure; and (6) consequences for invalid ratings.
These proposed changes do not impact the energy conservation standard.
DOE proposes to revise the test procedure such that tests of multi-
circuit products, triple-capacity northern heat pump products, and
multi-blower products can be performed without the need of an interim
waiver or a waiver. Existing interim waivers and waivers, as
applicable, regarding these products would terminate on the effective
date of a final rule promulgating the proposals in this SNOPR. DOE also
reaffirms that the waivers associated with multi-split products have
already terminated and that these products can also be tested using the
current and proposed test procedure. These proposed changes do not
impact the energy conservation standard and thus are proposed as part
of revisions to Appendix M.
DOE also proposes to clarify that air-to-water heat pump products
integrated with domestic water heating are not subject to central air
conditioner and heat pump energy conservation standards. Accordingly,
the waiver regarding these products would terminate effective 180 days
after publication of a final rule that incorporates the proposals in
this SNOPR.
DOE proposes revisions to the test methods and calculations for off
mode power consumption that were proposed or modified in the June 2010
NOPR, April 2011 SNOPR, and October 2011 SNOPR. These revisions address
comments received in response to the October 2011 SNOPR suggesting that
test methods and calculations more accurately represent off-mode power
consumption in field applications. These proposed changes do not impact
the energy conservation standard. Specifically, DOE proposes the
following:
(1) Establishment of separate testing and calculations that would
depend on whether the tested unit is equipped with a crankcase heater
and whether the crankcase heater is controlled during the test;
(2) Alteration of the testing temperatures such that the crankcase
heater is tested in outdoor air conditions that are representative of
the shoulder and heating seasons;
(3) Changing of the testing methodology for determining the power
consumption of the low-voltage components (PX);
(4) Changing of the calculation of the off mode power rating
(PW,OFF) such that the off mode power for the shoulder and heating
seasons are equally weighted;
(5) Implementation of a time delay credit for energy consumption,
including credits in the form of scaling factors and multipliers for
energy-efficient products that require larger crankcase heaters to
maintain product reliability;
(6) Addition of an alternative energy determination method for
determining off mode power for coil-only split-systems; and
(7) Inclusion of a means for calculating a basic model's annual off
mode energy use, from which manufacturers could make representations
about their products' off mode energy use.
DOE also proposes changes to improve the repeatability and reduce
the test burden of the test procedure. These proposed changes do not
impact the energy conservation standard. Specifically, DOE proposes the
following:
(1) Clarification of fan speed settings;
[[Page 69282]]
(2) Clarification of insulation requirements for refrigerant lines
and addition of a requirement for insulating mass flow meters;
(3) Addition of a requirement to demonstrate inlet air temperature
uniformity for the outdoor unit using thermocouples;
(4) Addition of a requirement that outdoor air conditions be
measured using sensors measuring the air captured by the air sampling
device(s) rather than the temperature sensors located in the air stream
approaching the inlets;
(5) Addition of a requirement that the air sampling device and the
tubing that transfers the collected air to the dry bulb temperature
sensor be at least two inches from the test chamber floor, and a
requirement that humidity measurements be based on dry bulb temperature
measurements made at the same location as the corresponding wet bulb
temperature measurements used to determine humidity;
(6) Clarification of maximum speed for variable-speed compressors;
(7) Addition of requirements that improve consistency of
refrigerant charging procedures;
(8) Allowance of an alternative arrangement for cyclic tests to
replace the currently-required damper in the inlet portion of the
indoor air ductwork for single-package ducted units;
(9) Clarification of the proper supply voltage for testing;
(10) Revision of the determination of the coefficient of cyclic
degradation (CD);
(11) Option for a break-in period of up to 20 hours;
(12) Update of references to industry standards where appropriate;
(13) Withdrawal of all references to ASHRAE Standard 116-1995;
(14) Inclusion of information from the draft AHRI 210/240; and
(15) Provisions regarding damping of pressure transducer signals to
avoid exceeding test operating tolerances due to high frequency
fluctuations.
Lastly, DOE proposes clarifications of any sections of the test
procedure that may be ambiguous. Specifically, DOE proposes to add
reference to an industry standard for testing variable refrigerant flow
multi-split systems; replace the informative guidance table for using
the test procedure; and clarify definitions of multi-split systems and
mini-split systems, which DOE now proposes to call single-zone-
multiple-unit systems. These proposed changes do not impact the energy
conservation standard.
DOE notes that all the above-listed proposed changes to the test
procedure would not impact the energy conservation standard and as such
are proposed as part of a revised Appendix M. Given the extensive
changes proposed for Appendix M, DOE has provided a full re-print of
Appendix M in the regulatory text of this SNOPR that includes the
changes proposed in this SNOPR as well as those proposed in the June
2010 NOPR and the April 2011 and October 2011 SNOPRs that have not been
withdrawn.
DOE also proposes various changes to the test procedure that would
affect the energy conservation standard and proposes incorporating
these changes in a new appendix, Appendix M1 to Subpart B of 10 CFR
part 430, which includes the text of Appendix M to Subpart B of 10 CFR
part 430 with amendments as proposed in this SNOPR. Specifically, DOE
proposes the following:
(1) Increase the minimum external static pressure requirements for
conventional central air conditioners and heat pumps to better
represent the external static pressure conditions in field
installations; \4\
---------------------------------------------------------------------------
\4\ Conventional central air conditioners and heat pumps are
those products that are not short duct systems (see section III.F.2)
or small-duct, high-velocity systems.
---------------------------------------------------------------------------
(2) Add a minimum external static pressure adjustment to correct
for potentially unrepresentative external static pressure conditions
for blower coil systems tested with condensing furnaces;
(3) Raise the default fan power for coil-only systems;
(4) Adjust the heating load line equation such that the zero load
point occurs at 55 [deg]F for Region IV, the adjustment factor is 1.3,
and the heating load is tied with the heat pump's cooling capacity; and
(5) Revise the heating mode test procedure to allow more options
for products equipped with variable-speed compressors.
DOE proposes to make the test procedure revisions in this SNOPR as
reflected in the revised Appendix M to Subpart B of 10 CFR part 430
effective on a date 180 days after publication of the test procedure
final rule in the Federal Register and mandatory for testing to
determine compliance with the existing energy conservation standards
for central air conditioners and heat pumps as of that date. DOE
proposes to make the test procedure revisions in this SNOPR as
reflected in the proposed new Appendix M1 to Subpart B of 10 CFR part
430 effective on the compliance date of the revised energy conservation
standards for central air conditioners and heat pumps and mandatory for
testing to determine compliance with said revised standards as of that
date. DOE will address any comments received in response to this SNOPR
in the test procedure final rule.
As noted in section I.A, 42 U.S.C. 6293(e) requires that DOE shall
determine to what extent, if any, the proposed test procedure would
alter the measured energy efficiency and measured energy use. DOE has
determined that some of these proposed amendments would result in a
change in measured energy efficiency and measured energy use for
central air conditioners and heat pumps. Therefore, DOE is conducting a
separate rulemaking to amend the energy conservation standards for
central air conditioners and heat pumps with respect to the revised
test procedure, once its proposals become final. (Docket No. EERE-2014-
BT-STD-0048)
III. Discussion
This section discusses the revisions to the certification
requirements and test procedure that DOE proposes in this SNOPR.
A. Definitions, Testing, Rating, and Compliance of Basic Models of
Central Air Conditioners and Heat Pumps
On August 19 and 20, 2014, DOE issued two draft guidance documents
regarding the test procedure for central air conditioners and heat
pumps. One guidance document dealt with testing and rating split
systems with blower coil indoor units (Docket No. EERE-2014-BT-GUID-
0033); and the other dealt more generally with selecting units for
testing, rating, and certifying split-system combinations, including
discussion of basic models and of condensing units and evaporator coils
sold separately for replacement installation (Docket No. EERE-2014-BT-
GUID-0032). The comments in response to these draft guidance documents
are discussed in this section of the notice. DOE has proposed changes
to the substance of the draft guidance that reflects the comments
received as well as the recommendations of the regional standards
enforcement Working Group (Docket No. EERE-2011-BT-CE-0077-0070,
Attachment). The proposed changes supplant the two draft guidance
documents; DOE will not finalize the draft guidance documents and
instead will provide any necessary clarity through this notice and the
final rule.
1. Basic Model Definition
In the August 20, 2014 draft guidance document (Docket No. EERE-
2014-BT-GUID-0032), DOE clarified that a basic
[[Page 69283]]
model means all units of a given type (or class thereof) having the
same primary energy source, and which have essentially identical
electrical, physical, and functional characteristics that affect energy
efficiency. 10 CFR 430.2. DOE noted that for split-system units, this
includes a condensing (outdoor) unit and a coil-only or blower coil
indoor unit.\5\
---------------------------------------------------------------------------
\5\ DOE notes that a blower coil indoor unit may consist of
separate units, one that includes the indoor coil and another that
is an air mover, either a modular blower or a furnace.
Alternatively, a blower coil indoor unit may be a single unit that
includes both the indoor coil and the indoor fan. Hence, in further
discussion, ``blower coil indoor unit'' may be any one of these
three options.
---------------------------------------------------------------------------
In the guidance document, DOE also stated that if a company
intended to claim ratings for each combination of outdoor unit and
indoor unit, it must certify all possible model combinations as
separate basic models. Only the basic model combinations that include a
highest sales volume combination (HSVC) indoor unit for a given outdoor
unit must be tested, while the other basic models may be rated with an
ARM. Alternatively, the manufacturer could make all combinations of a
given model of outdoor unit part of the same basic model and not rate
all individual combinations. However, all combinations within the basic
model would have to have the same represented efficiency, based on the
least efficient combination. This association would be included in the
certification report.
In response to the draft guidance document, AHRI and Johnson
Controls (JCI) stated that there was a difference between DOE's
definition of Basic Model and the industry's use of Basic Model Groups
(Docket No. EERE-2014-BT-GUID-0032, AHRI, No. 8 at p. 1; JCI, No. 5 at
p. 3) Johnson Controls specified that most manufacturers consider a
specific outdoor model with all combinations of indoor units to be a
basic model and notes that DOE's definition appeared to allow outdoor
units to be combined into a basic model if they share the same ratings.
(Id.)
DOE reviewed AHRI's Operations Manual for Unitary Small Air-
Conditioners and Air-Source Heat Pumps (Includes Mixed-Match Coils)
(Rated Below 65,000 Btu/h) Certification Program (AHRI OM 210/240--
January 2014).\6\ This document specifies the following definitions:
---------------------------------------------------------------------------
\6\ Available at: www.ahrinet.org/App_Content/ahri/files/Certification/OM%20pdfs/USE_OM.pdf (Last accessed March 20, 2015.)
A Split System BMG [Basic Model Group \7\] consists of products
with the same Outdoor Unit used with several Indoor Unit
combinations (i.e. horizontal, vertical, A-coil, etc.). Same Outdoor
Unit refers to models with the same or comparable compressor, used
with the same outdoor coil surface area and the same outdoor air
quantity.
---------------------------------------------------------------------------
\7\ According to the AHRI General Operations Manual, a basic
model is a product possessing a discrete performance rating, whereas
a basic model group is a set of models that share characteristics
that allow the performance of one model to be representative of the
group, although the group does not have to share discrete
performance. (General OM--October 2013). Available at:
www.ahrinet.org/App_Content/ahri/files/Certification/OM%20pdfs/General_OM.pdf. (Last accessed March 24, 2015.)
---------------------------------------------------------------------------
An ICM [Independent Coil Manufacturer] BMG consists of coils
(Indoor Units) with matching capacity ranges of 6,000 Btu/h and the
following identical geometry parameters: Air-handler, evaporator fan
type, evaporator number of rows, type of equipment (air-cooled,
water-cooled or evaporatively-cooled), evaporator tube centers,
evaporator fin types, evaporator fins/inch, evaporator tube OD,
evaporator expansion device, fin length per slab, fin height per
slab, number of slabs in the coil, fin material type, tube material
type, and total number of active tubes (refer to Table H1).
In order to create consistency within the industry, DOE proposes to
modify its basic model definition for central air conditioners and heat
pumps. Specifically, DOE proposes that manufacturers would have a
choice in how to assign individual models (for single-package units) or
combinations (for split systems) to basic models. Specifically,
manufacturers may consider each individual model/combination its own
basic model, or manufacturers may assign all individual models of the
same single-package system or all individual combinations using the
same model of outdoor unit (for outdoor unit manufacturers (OUM)) or
model of indoor unit (for independent coil manufacturers (ICM)) to the
same basic model.
DOE believes that this proposal is consistent with the existing
general definition of basic model which refers to all units having the
same primary energy source and having essentially identical electrical,
physical, and functional characteristics that affect energy consumption
or energy efficiency. However, DOE proposes to further define the
physical characteristics necessary to assign individual models or
combinations to the same basic model:
(i) For split-systems manufactured by independent coil
manufacturers (ICMs) and for small-duct, high velocity systems: All
individual combinations having the same model of indoor unit, which
means the same or comparably performing indoor coil(s) [same face area;
fin material, depth, style (e.g. wavy, louvered), and density (fins per
inch); tube pattern, material, diameter, wall thickness, and internal
enhancement], indoor fan(s) [same air flow with the same indoor coil
and external static pressure, same power input], auxiliary
refrigeration system components if present (e.g. expansion valve), and
controls.
(ii) for split-systems manufactured by outdoor unit manufacturers
(OUMs): All individual combinations having the same model of outdoor
unit, which means the same or comparably performing compressor(s) [same
displacement rate (volume per time) and same capacity and power input
when tested under the same operating conditions], outdoor coil(s) [same
face area; fin material, depth, style (e.g. wavy, louvered), and
density (fins per inch); tube pattern, material, diameter, wall
thickness, and internal enhancement], outdoor fan(s) [same air flow
with the same outdoor coil, same power input], auxiliary refrigeration
system components if present (e.g. suction accumulator, reversing
valve, expansion valve), and controls.
The proposed requirements for single-package models combine the
requirements listed describing the characteristics of the same models
of indoor units and same models of outdoor units. DOE requests comment
on its proposal to modify the definition of ``basic model'', as well as
the proposed physical characteristics required for assigning individual
models or combinations to the same basic model, as described above.
If manufacturers assign each individual model or combination to its
own basic model, DOE proposes that each individual model/combination
must be tested and that an AEDM cannot be applied. This option would
limit a manufacturer's risk in terms of noncompliance but would
represent increased testing burden compared to the other option.
If manufacturers assign all individual combinations of a model of
outdoor unit (for OUMs) or model of indoor unit (for ICMs) to a single
basic model, DOE further proposes that, in contrast to the draft
guidance document and DOE's current regulations, each individual
combination within a basic model (i.e., having the same model of
outdoor unit for OUMs, or having the same model of indoor unit for
ICMs) must be certified with a rating determined for that individual
combination. In other words, individual combinations within the same
basic model that have different SEER ratings, for example, would be
certified with their individual ratings, rather than with the lowest
SEER of the basic model. However, only one individual combination in
each basic
[[Page 69284]]
model would have to be tested (see section III.A.3.a), while the others
may be rated using an AEDM. This option reduces testing burden but
increases risk. Specifically, if any one of the combinations within a
basic model fails to meet the applicable standard, then all of the
combinations within the basic model fail, and the entire basic model
must be taken off the market (i.e., the model of outdoor unit for OUMs
and the model of indoor unit for ICMs). All combinations offered for
sale (e.g., for OUMs, based on a given model of outdoor unit which is
the basis of the basic model) must be certified, and all of these
combinations within the basic model must meet applicable standards. DOE
notes that under this proposed rule, ICMs and OUMs will continue to
have an independent obligation to test, provide certified ratings, and
ensure compliance with applicable standards.
By way of example, a manufacturer has two models of outdoor units,
models A and B. Each of models A and B can be paired with any of three
models of indoor units--models 1, 2, and 3. Per the guidance document,
the manufacturer could either: (1) Make each combination a separate
basic model (i.e., A-1, A-2, A-3, B-1, B-2, and B-3), test the HSVC for
each model of outdoor unit (A and B), and rate the other basic models
with an ARM; (2) make each combination a separate basic model and test
each of them; or (3) make combinations A-2 and A-3 part of basic model
A-1 (and similarly B-2 and B-3 part of B-1) and represent the
efficiency of all three with the same certified rating at the least
efficient combination in the basic model. In this proposal, the
manufacturer could either: (1) Make each combination a separate basic
model and test and rate each combination; or (2) make combinations A-2
and A-3 part of basic model A-1 (and similarly B-2 and B-3 part of B-
1), test the HSVC combination for the model of outdoor unit, and test
or use an AEDM to rate the efficiency of all other combinations in the
basic model.
DOE notes that unlike in the current ``basic model'' definition
that contains less detail on what constitutes essentially identical
characteristics, under DOE's new proposal, manufacturers would not be
able to assign different models of outdoor units (for OUMs) or models
of indoor units (for ICMs) to a single basic model Based on a review of
certification data, it appears that most manufacturers are not
currently doing this, so DOE expects this proposal to have limited
impact on current practices.
Additional rating and certification requirements for single-package
models and multi-split, multi-circuit, and single-zone-multiple-coil
models are described in section III.A.3.c.
Revisions to the test procedure as proposed in section III.D of
this SNOPR enable the determination of off mode power consumption,
which reflects the operation of the contributing components: Crankcase
heater and low-voltage controls. Varying designs of these components
produce different off mode power consumption. DOE proposes that if
individual combinations that are otherwise identical are offered with
multiple options for off mode related components, manufacturers at a
minimum must rate the individual combination with the crankcase heater
and controls which are the most consumptive (i.e., would result in the
largest value of PW,OFF). If a manufacturer wishes to also
make representations for less consumptive off mode options for the same
individual combination, the manufacturer may provide separate ratings,
but the manufacturer must differentiate the individual model numbers
for these ratings. These individual combinations would be within the
same basic model. DOE discusses this in relation to single-package
units in section III.A.3.e.
DOE also proposes to clarify that a central air conditioner or
central air conditioning heat pump may consist of: A single-package
unit; an outdoor unit and one or more indoor units (e.g., a single-
split or multi-split system); an indoor unit only (rated as a
combination by an ICM with an OUM's outdoor unit); or an outdoor unit
only (with no match, rated by an OUM with the coil specified in this
test procedure). DOE has proposed adding these specifications to the
definition of central air conditioner or central air conditioning heat
pump in 10 CFR 430.2. In the certification reports submitted by OUMs
for split systems, DOE proposes that manufacturers must report the
basic model number as well as the individual model numbers of the
indoor unit(s) and the air mover where applicable.
2. Additional Definitions
In order to specify differences in the proposed basic model
definition for ICMs and OUMs, DOE also proposes the following
definitions:
Independent coil manufacturer (ICM) means a manufacturer that
manufactures indoor units but does not manufacture single-package
units or outdoor units.
Outdoor unit manufacturer (OUM) means a manufacturer of single-
package units, outdoor units, and/or both indoor units and outdoor
units.
With respect to any given basic model, a manufacturer could be an
ICM or an OUM. DOE notes that the use of the term ``manufacturer'' in
these definitions refers to any person who manufactures, produces,
assembles, or imports a consumer product. See 42 U.S.C. 6291(10, 12).
DOE also proposes to define variable refrigerant flow (VRF) systems
as a kind of multi-split system. DOE notes that not all VRF systems are
commercial equipment. Therefore, the proposed definition also clarifies
that VRF systems that are single-phase and less than 65,000 btu/h are a
kind of central air conditioners and central air conditioning heat
pumps.
DOE also proposes to modify the definition of indoor unit. DOE
noted in market research that ICMs may not always provide cooling mode
expansion devices with indoor units. Therefore to provide clarity in
the testing and rating requirements, DOE proposes to change the
definition of ``indoor unit'' to clarify that it may not include the
cooling mode expansion device. Also, for reasons discussed in section
III.A.3.f, DOE proposes to include the casing in the definition so that
uncased coils will not be considered indoor units:
Indoor unit transfers heat between the refrigerant and the
indoor air, and consists of an indoor coil and casing and may
include a cooling mode expansion device and/or an air moving device.
DOE proposes to specify in Appendix M that if the indoor unit does
not ship with a cooling mode expansion device, the system should be
tested using the device as specified in the installation instructions
provided with the indoor unit, or if no device is specified, using a
TXV. DOE notes that the AHRI program does not appear to assume that the
expansion device is necessarily provided with the coil, i.e., AHRI's
operations manual specifies that for testing for the AHRI certification
program, the ICM must provide an indoor coil and expansion device.
Finally, DOE is proposing to clarify several other definitions
currently in 10 CFR 430.2 with minor wording changes and move them to
10 CFR 430, Subpart B, Appendix M. The proposed definition of central
air conditioner or central air conditioning heat pump in 10 CFR 430.2
refers the reader to the additional central air conditioner-related
definitions in Appendix M. Locating all of the relevant definitions in
the appendix will make it easier to find and reference them. DOE also
proposes to remove entirely the definitions for ``condenser-evaporator
coil combination'' and ``coil family'' as
[[Page 69285]]
those terms no longer appear in the proposed regulations.
3. Determination of Certified Rating
During the regional standards Working Group meetings, participants
invested a great deal of time and energy discussing the relationship
between system ratings and an effective enforcement plan. As part of
the negotiations, the Working Group requested that DOE issue guidance
regarding the applicability of regional standards to indoor units and
outdoor units distributed separately and the applicability of regional
standards to different combinations of indoor and outdoor units. DOE
developed two draft guidance documents to address these issues. After
consideration of the Working Group's discussions and the comments
received on the two draft guidance documents, DOE determined that
regulatory changes would be necessary to implement the approach agreed
to by the Working Group. DOE is proposing several of those regulatory
changes as part of this rulemaking. The remainder of the necessary
regulatory changes will be addressed in a forthcoming regional
standards enforcement notice of proposed rulemaking.
During the pendency of the rulemakings (CAC TP and Regional
Standards), DOE reaffirms its commitment to the approach advocated by
the Working Group, subject to consideration of comments received in the
rulemakings to effectuate the necessary changes to the regulations. The
following sections describe the two guidance documents and DOE's
proposals to address them as part of this rulemaking.
a. Single-Split-System Air Conditioners Rated by OUMs
In the August 20, 2014 draft guidance document (Aug 20 Guidance)
(EERE-2014-BT-GUID-0032), DOE proposed to clarify that when selecting
which split-system air conditioner and heat pump units to test (in
accordance with the DOE test procedure), a unit of each outdoor model
must be paired with a unit of one selected indoor model. 10 CFR
429.16(a)(2)(i). Specifically, the manufacturer must test the
condenser-evaporator coil combination that includes the model of
evaporator coil that is likely to have the largest volume of retail
sales with the particular model of condensing unit. 10 CFR
429.16(a)(2)(ii) (This combination is also known as the highest sales
volume combination or HSVC.) That is, the HSVC for each condensing unit
may not be rated using an ARM. (See section III.B regarding DOE's
proposal to switch from ARMs to AEDMs for this product.)
The guidance further stated that for any other split-system
combination that includes the same outdoor unit model but a different
indoor unit model than the HSVC, manufacturers may determine
represented values of energy efficiency (including those values that,
for each combination, must be reported in certifications to DOE) of a
split-system central air conditioner or heat pump basic model
combination either by testing the combination in accordance with the
DOE test procedure or by applying an ARM that has been approved by DOE
in accordance with the provisions of 10 CFR 429.70(e)(1) and (2). 10
CFR 429.16(a)(2)(ii)(A) and (B)(1).
In the August 19, 2014 draft guidance document (August 19 Guidance)
(EERE-2014-BT-GUID-0033), DOE proposed to clarify that split-system
central air conditioners other than those with single-speed compressors
may be tested and rated using a blower coil only if the condensing unit
is sold exclusively for use with a blower coil indoor unit. 10 CFR
429.16(a)(2)(ii). The guidance stated that there is no provision in the
Code of Federal Regulations (CFR) permitting use of a blower coil for
testing and rating a split-system central air conditioner where the
condensing unit is also offered for sale with a coil-only indoor unit,
and that, furthermore, there is no provision in the CFR permitting the
use of a blower coil for testing and rating a condensing unit with a
single-speed compressor.
Commenters generally agreed with the information in the August 20
Guidance regarding selecting units for testing, rating, and certifying
split-system combinations. In addition, in response to the August 19
Guidance, DOE received nearly identical comments from several
stakeholders generally agreeing with the intent of the guidance to
emphasize that single-speed compressor products must be tested and
rated with a coil-only system as HSVC. (Docket No. EERE-2014-BT-GUID-
0033, AHRI No. 8 at p. 2; Nordyne, No. 9 at p. 1; Lennox, No. 4 at p.
2; Ingersoll Rand, No. 3 at p. 1; Goodman, No. 10 at p. 1; Rheem, No. 2
at p. 2; JCI, No. 5 at p. 2-3) These stakeholders, as well as Mortex,
clarified that other combinations besides the HSVC, including blower
coil combinations, can be rated through testing or using an ARM. (Id.;
Mortex, No. 6 at p. 1) Stakeholders recommended language identical to
or similar to the following:
Split-system central air conditioners with single-speed
compressors must be tested and rated using a coil-only for the HSVC.
10 CFR 429.16(a)(2)(ii). Such single-speed systems may be rated with
other coil-only and blower coil indoor units through the use of a
DOE approved ARM or by testing. 10 CFR 429.16(a)(2)(ii)(A) and 10
CFR 429.16(a)(2)(ii)(B). Furthermore, there is no provision in the
CFR permitting the use of a blowercoil for testing and rating a
condensing unit with a single-speed compressor for the HSVC, unless:
[Version 1] the unit is a mini-split, multi-split or
through-the-wall, OR
[Version 2] the unit is sold and installed only with
blower-coil indoor units.
(Version 1: Docket No. EERE-2014-BT-GUID-0033, Lennox, No. 4 at
p. 2; Ingersoll Rand, No. 3 at p. 2; Goodman, No. 10 at p. 3; Rheem,
No. 2 at p. 3; JCI, No. 5 at p. 4; Version 2: AHRI No. 8 at p. 3;
Nordyne, No. 9 at p. 2)
AHRI and several manufacturers disputed that when using a
compressor other than single speed, the HSVC can never be a blower coil
unless it is exclusively used with a blower coil. AHRI and the
manufacturers reported that many multi-stage capacity products are
tested and rated with high efficiency blower coil or furnace products
as the HSVC even though those systems are also rated for coil-only use.
(Docket No. EERE-2014-BT-GUID-0033, AHRI No. 8 at p. 2; Nordyne, No. 9
at p. 2; Lennox, No. 4 at p. 2; Ingersoll Rand, No. 3 at p. 2; Goodman,
No. 10 at p. 2; Rheem, No. 2 at p. 2; Carrier, No. 7 at p. 1) Johnson
Controls responded that they test and rate multi-speed compressor units
with blower coils or furnace/coils as the HSVC. (JCI, No. 5 at p. 3).
AHRI and the manufacturers reported that not allowing this could limit
the application of high performing products, and that it is important
for units designed for blower coil to also be rated as coil-only to
offer certain consumers a compromise of cost and performance. AHRI and
the manufacturers proposed the following modified language:
Split-system central air conditioners other than those with
single-speed compressors (two-stage or multi-stage) may be tested
and rated using a blower-coil only as HSVC only if the condensing
unit design intent is for use with a blower-coil indoor unit (e.g.
the evaporator coil that is likely to have the largest volume of
retails sales with the particular model of condensing unit is a
blower-coil).
(Docket No. EERE-2014-BT-GUID-0033, AHRI No. 8 at p. 3; Nordyne, No.
9 at p. 2; Lennox, No. 4 at p. 3; Ingersoll Rand, No. 3 at p. 2;
Goodman, No. 10 at p. 3; Rheem, No. 2 at p. 3; JCI, No. 5 at p. 4;
Carrier, No. 7 at p. 2 with slightly different language)
After reviewing the comments, DOE proposes to make changes to 10
CFR 429.16 to revise the testing and rating requirements for single-
split-system air conditioners. (See section III.F.4
[[Page 69286]]
regarding discussion of new definitions including ``single-split-
system.'') These changes will occur in two phases. In the first phase,
prior to the compliance date of any amended energy conservation
standards, DOE proposes only a slight change to the current
requirements. Specifically, DOE proposes that for single-split-system
air conditioners with single capacity condensing units, each model of
outdoor unit must be tested with the model of coil-only indoor unit
that is likely to have the largest volume of retail sales with the
particular model of outdoor unit. For split-system air conditioners
with other than single capacity condensing units each model of outdoor
unit must also be tested with the model of coil-only indoor unit likely
to have the largest sales volume unless the model of outdoor unit is
sold only with model(s) of blower coil indoor units, in which case it
must be tested and rated with the model of blower coil indoor unit
likely to have the highest sales volume. However, any other combination
may be rated through testing or use of an AEDM. (See section III.B
regarding proposed changes from ARM to AEDM.) Therefore, both single
capacity and other than single capacity systems may be rated with
models of both coil-only or blower coil indoor units, but if the system
is sold with a model of coil-only indoor unit, it must, at a minimum,
be tested in that combination.
In the second phase, DOE anticipates that any amended energy
conservation standards will be based on blower coil ratings. Therefore,
DOE proposes that all single-split-system air conditioner basic models
be tested and rated with the model of blower coil indoor unit likely to
have the largest volume of retail sales with that model of outdoor
unit. Manufacturers would be required to also rate all other blower
coil and coil-only combinations within the basic model but would be
permitted do so through testing or an AEDM. DOE believes that this
proposal will offer the benefits of design for high performance through
the use of blower coils as well as providing appropriate
representations for coil-only combinations. In addition, given that
most basic models are currently submitted as blower coil ratings, this
change will align DOE requirements with industry practice. This
proposed change would also be accounted for in the parallel energy
conservation standards rulemaking, and is contingent upon any proposed
amended standards being based on blower coil ratings.
Table III.1 summarizes these proposed changes.
Table III.1--Test Requirements for Single-Split-System Non-Space-Constrained Air Conditioners Rated by OUMs
----------------------------------------------------------------------------------------------------------------
Date Equipment type Must test each: With:
----------------------------------------------------------------------------------------------------------------
Before the compliance date for any Split-System AC with Model of Outdoor Unit. The model of coil-only
amended energy conservation single capacity indoor unit that is likely
standards. condensing unit. to have the largest volume
of retail sales with the
particular model of
outdoor unit.
Split-System AC with Model of Outdoor Unit. The model of coil-only
other than single indoor unit that is likely
capacity condensing to have the largest volume
unit. of retail sales with the
particular model of
outdoor unit, unless the
model of outdoor unit is
only sold with model(s) of
blower coil indoor units
in which case, the model
of blower coil indoor unit
that is likely to have the
largest volume of retail
sales with the particular
model of outdoor unit.
After the compliance date for any Split-system AC....... Model of Outdoor Unit. The model of blower coil
amended energy conservation indoor unit that is likely
standards. to have the largest volume
of retail sales with the
particular model of
outdoor unit.
----------------------------------------------------------------------------------------------------------------
In order to facilitate these changes, DOE also proposes definitions
of blower coil indoor unit and coil-only indoor unit:
Blower coil indoor unit means the indoor unit of a split-
system central air conditioner or heat pump that includes a
refrigerant-to-air heat exchanger coil, may include a cooling-mode
expansion device, and includes either an indoor blower housed with the
coil or a separate designated air mover such as a furnace or a modular
blower (as defined in Appendix AA).
Blower coil system refers to a split-system that includes
one or more blower coil indoor units.
Coil-only indoor unit means the indoor unit of a split-
system central air conditioner or heat pump that includes a
refrigerant-to-air heat exchanger coil and may include a cooling-mode
expansion device, but does not include an indoor blower housed with the
coil, and does not include a separate designated air mover such as a
furnace or a modular blower (as defined in Appendix AA). A coil-only
indoor unit is designed to use a separately-installed furnace or a
modular blower for indoor air movement.
Coil-only system refers to a system that includes one or
more coil-only indoor units.
DOE notes that these proposed testing requirements, when combined
with the proposed definition for basic model, require that each basic
model have at least one rating determined through testing; no basic
model can be rated solely using an AEDM.
DOE also proposes that in the certification report, manufacturers
state whether each rating is for a coil-only or blower coil
combination.
DOE seeks comment on its proposed changes to the determination of
certified ratings for single-split-system air conditioners when rated
by an OUM, as well as on the proposed definitions for blower coil and
coil-only indoor units.
b. Split-System Heat Pumps and Space-Constrained Split Systems
The current requirements for split-system heat pumps in 10 CFR
429.16 require testing a condenser-evaporator coil combination with the
evaporator coil likely to have the largest volume of retail sales with
the particular model of condensing unit. The coil-only requirement does
not apply to split-system heat pumps, because central heat pump indoor
units nearly always include both a coil and a fan.
In this notice, DOE proposes to slightly modify the wording
explaining this requirement; specifically, the requirement would use
the more general terms ``indoor unit'' and ``outdoor unit,'' rather
than ``evaporator coil'' and ``condensing unit,'' since the requirement
addresses heat pumps. DOE also proposes to apply this same test
requirement to space-constrained split-system air conditioners and heat
pumps. The current requirements in 10 CFR
[[Page 69287]]
429.16 do not specifically call out space-constrained systems, and as
such, the current coil-only requirements for split-system air
conditioners apply to space-constrained split-system air conditioners.
Therefore, this proposal will change test procedures for space-
constrained split-system air conditioners but will not change, other
than in nomenclature, the test procedures for space-constrained split-
system heat pumps.
c. Multi-Split, Multi-Circuit, and Single-Zone-Multiple-Coil Units
The current requirements in 10 CFR 429.16(a)(2)(ii) specify that
multi-split systems and mini-split systems designed to always be
installed with more than one indoor unit (now proposed to be called
single-zone-multiple-coil units, see section III.F.4) be tested using a
``tested combination'' as defined in 10 CFR 430.2. For multi-split
systems, each model of condensing unit currently must be tested with a
non-ducted tested combination and a ducted tested combination.
Furthermore, current requirements for testing with a coil-only indoor
unit do not apply to mini-splits or multi-splits, as the general use of
these terms in the industry refers to specific types of systems with
blower coil indoor units. Id.
The current requirements also state that for other multi-split
systems that include the same model of condensing unit but a different
set of evaporator coils, whether the evaporator coil(s) are
manufactured by the same manufacturer or by a component manufacturer
(i.e., ICM), the rating must be: (1) Set equal to the rating for the
non-ducted indoor unit system tested (for systems composed entirely of
non-ducted units), (2) set equal to the rating for the ducted indoor
unit system tested (for systems composed entirely of ducted units), or
(3) set equal to the mean of the values for the two systems (for
systems having a mix of non-ducted and ducted indoor units). (10 CFR
429.16(a)(2)(ii))
In this notice, DOE proposes a slight modification to the testing
requirements for single-zone-multiple-coil and multi-split systems, and
adds similar requirements for testing multi-circuit systems (see
section III.C.2 for more information about these systems). DOE also
clarifies that these requirements apply to VRF systems that are single-
phase and less than 65,000 Btu/h (see section III.A.3.c for more
details). For all multi-split, multi-circuit, and single-zone-multiple-
coil split systems, DOE proposes that at a minimum, each model of
outdoor unit must be tested as part of a tested combination (as defined
in the CFR) composed entirely of non-ducted indoor units. For any
models of outdoor units also sold with short-ducted indoor units, a
second ``tested combination'' composed entirely of short-ducted indoor
units would be required to be tested. DOE also proposes the
manufacturers may rate a mixed non-ducted/short-ducted combination as
the mean of the represented values for the tested non-ducted and short-
ducted combinations.
Under the proposed definition of basic model, these three
combinations (non-ducted, short-ducted, and mixed) would represent a
single basic model. When certifying the basic model, manufacturers
should report ``* * *'' for the indoor unit model number, and report
the test sample size as the total of all the units tested for the basic
model, not just the units tested for each combination. For example, if
the manufacturer tests 2 units of a non-ducted combination and 2 units
of a short-ducted combination, and also rates a mix-match combination,
the manufacturer should specify ``4'' as the test sample size for the
basic model, while providing the rating for each combination. DOE also
proposes that manufacturers be allowed to test and rate specific
individual combinations as separate basic models, even if they share
the same model of outdoor unit. In this case, the manufacturer must
provide the individual model numbers for the indoor units rather than
stating ``* * *''. Table III.2 provides an example of both situations.
Table III.2--Example Ratings for Multi-Split Systems
--------------------------------------------------------------------------------------------------------------------------------------------------------
Individual model Individual model Non-ducted
Basic model (outdoor unit) (indoor unit) Sample size Ducted rating rating Mix rating
--------------------------------------------------------------------------------------------------------------------------------------------------------
ABC.................................. ABC..................... * * *.................. 4 14 15 14.5
ABC1................................. ABC..................... 2-A123; 3-JH746........ 2 .............. 17 ..............
--------------------------------------------------------------------------------------------------------------------------------------------------------
DOE requests comment on whether additional requirements are
necessary for multi-split systems paired with models of conventional
ducted indoor units rather than short-duct indoor units.
DOE also notes that the test procedure currently allows testing of
only non-ducted or short-ducted systems, and not combinations of the
two. Therefore to rate individual mix-match combinations, manufacturers
would have to test 4 units--2 ducted and 2 short-ducted. DOE requests
comment on whether manufacturers should have the ability to test mix-
match systems using the test procedure rather than rating them using an
average of the other tested systems. DOE also requests comment on
whether manufacturers should be able to rate mix-match systems using
other than a straight average, such as a weighting by the number of
non-ducted or short-ducted units. Finally, DOE requests comment on
whether the definition of ``tested combination'' is appropriate for
rating specific individual combinations, or whether manufacturers
should be given more flexibility, such as testing with more than 5
indoor units.
In reviewing the market for multi-split systems, DOE determined
that some are sold by OUMs with only models of small-duct, high
velocity (SDHV) indoor units, or with a mix of models of short-duct and
SDHV units. (See section III.F.2 regarding the proposed definition of
short ducted systems.) These kinds of units are not currently
explicitly addressed in DOE's test requirements. Therefore, DOE
proposes to add a requirement that for any models of outdoor units also
sold with models of SDHV indoor units, a ``tested combination''
composed entirely of SDHV indoor units must be used for testing and
rating. However, such a system must be certified as a different basic
model.
DOE notes that multi-split systems consisting of a model of outdoor
unit paired with models of non-ducted or short-ducted units must meet
the energy conservation standards for split-system air conditioners or
heat pumps, while systems consisting of a model of outdoor unit paired
with models of small-duct, high-velocity indoor units must meet SDHV
standards. DOE proposes to add a limitations section in 429.16 that
would require models of outdoor units that are rated and distributed in
combinations that span multiple product classes to be tested and
certified as compliant with the
[[Page 69288]]
applicable standard for each product class. Even if a manufacturer
sells a combination including models of both SDHV and other non-ducted
or short-ducted indoor units, DOE proposes that the manufacturer may
not provide a mix-match rating for such combinations. DOE requests
comment on whether manufacturers would want to rate such combinations,
and if so, how they would prefer to rate them (i.e., by by taking the
mean of a sample of tested non-ducted units and a sample of tested SDHV
units or by testing a combination on non-ducted and SDHV units), and
whether the SDHV or split-system standard would be most appropriate.
DOE understands that manufacturers of multi-split systems commonly
only test one sample rather than complying with the sampling plan
requirements in 429.16(a)(2)(i), which require a sample of two. DOE may
consider moving toward a single unit sample for single-zone multiple-
coil and multi-split system models, but in order to do so, DOE requires
information on manufacturing and testing variability associated with
these systems. In particular, DOE requires data to allow it to
understand how a single unit sample may be representative of the
population. DOE also requests information on what tolerances would need
to be applied to the ratings of these units based on a single unit
sample in order to account for the variability.
d. Basic Models Rated by ICMs
The current requirements in 10 CFR 429.16(a) require that each
condensing unit of a split system must be tested using the HSVC
associated with that condensing unit. There are no current requirements
for testing each model of indoor unit of a split system. Non-HSVC
combinations can be rated using an ARM, assuming the condensing unit of
the combination has a separate HSVC rating based on testing. DOE
understands that ICMs typically do not test all of their models of
indoor units, but rather use OUM test data for outdoor units to
generate ratings for their models. (See section III.B on AEDMs for
further information.) In this notice, DOE proposes that ICMs must test
and provide certified ratings for each model of indoor unit (i.e.,
basic model) with the least-efficient model of outdoor unit with which
it will be paired, where the least- efficient model of outdoor unit is
the outdoor unit in the lowest-SEER combination as certified by the
OUM. If more than one model of outdoor unit (with which the ICM wishes
to rate the model of indoor unit) has the same lowest-SEER rating, the
ICM may select one for testing purposes. This applies to both
conventional (i.e., non-short-duct, non-SDHV) split-systems and SDHV
systems. ICMs must rate all other individual combinations of the same
model of indoor unit, but may determine those ratings through testing
or use of an AEDM.
DOE understands that this proposal would increase test burden for
ICMs beyond the testing they currently conduct to meet ARM validation
requirements. However, DOE believes this burden is outweighed by the
benefit of providing more accurate ratings for models of indoor units
sold by ICMs. Additional discussion regarding potential test
requirements for ICMs can be found in the stakeholder comments
regarding AEDMs in section III.B.5.
DOE understands that the proposed definition of basic model for an
ICM, including what constitutes the ``same'' model of indoor unit and
thus would be required to be tested, is important for accurately
assessing the test burden for manufacturers as a result of this test
proposal. DOE seeks comment on the basic model definition in section
III.A.1. DOE also seeks comment on the proposed testing requirements
for ICMs.
e. Single-Package Systems
In the current regulations, 10 CFR 429.16(a)(2)(i) states that each
single-package system a must have a sample of sufficient size tested in
accordance with the applicable provisions of Subpart B. In this notice,
DOE proposes that the lowest SEER individual model within each basic
model must be tested. DOE expects that in most cases, each single-
package system will represent its own basic model. However, based on
the proposal for the definition of basic model in section III.A.1, this
may not always be the case. DOE notes that regardless, AEDMs do not
apply to single-package models--manufacturers may either test and rate
each individual single-package model, or if multiple individual models
are assigned to the same basic model per the proposed requirements in
the basic model definition, the manufacturer would be required to test
only the lowest SEER individual model within the basic model and use
that to determine the rating for the basic model.
DOE requests comment on the likelihood of multiple individual
models of single-package units meeting the requirements proposed in the
basic model definition to be assigned to the same basic model. DOE also
requests comment on whether, if manufacturers are able to assign
multiple individual models to a single basic model, manufacturers would
want to use an AEDM to rate other individual models within the same
basic model other than the lowest SEER individual model. Finally, DOE
requests comment on whether manufacturers would want to employ an AEDM
to rate the off-mode power consumption for other variations of off-mode
associated with the basic model other than the variation tested.
DOE also proposes to specify this same requirement for space-
constrained single-package air conditioners and heat pumps, which are
currently not explicitly identified in the test requirement section.
f. Replacement Coils
DOE stated in the August 20 Guidance that an individual condensing
unit or coil must meet the current Federal standard (National or
regional) when paired with the appropriate other new part to make a
system when tested in accordance with the DOE test procedure and
sampling plan.
In response, AHRI and manufacturers commented that they believed
the intent of the guidance was to clarify how the outdoor section of a
split system used in a replacement situation can be tested and rated to
meet the appropriate efficiency requirements. However, they felt this
language should not apply to the indoor coil. AHRI stated that indoor
coil is rarely changed and when it is, such as for an irreparable leak,
it requires an exact replacement. In addition, they note that
warranties can extend up to 10 years. Commenters also expressed the
view that the guidance would not result in an improvement to installed
product efficiency. (Docket No. EERE-2014-BT-GUID-0032, AHRI, No. 8 at
pp. 2-3; Rheem, No. 2 at p. 3; Goodman, No. 10 at pp. 2-3; Ingersoll
Rand, No. 3 at p. 2; Lennox, No. 4 at p. 2; Nordyne, No. 9 at p. 2)
AHRI and the manufacturers recommended removing indoor coils from the
draft guidance language on replacement. (Id.; JCI, No. 5 at p. 6)
Johnson Controls added further detail that using the term coil does
not differentiate between service parts (listed with part numbers) and
finished component assemblies (listed as a coil model) or between
evaporator coils and condenser coils. Johnson Controls added that
replacement parts cannot be rated as a finished coil assembly because
the replacement parts do not contain sheet metal parts required to
complete the installation. They also added that where the physical
characteristics of an evaporator coil are significantly different when
compared to a new system, replacing the old evaporator coil with a new
coil model rather than a replacement part could result in increased
cost and reduced
[[Page 69289]]
performance, reliability, and comfort. (Docket No. EERE-2014-BT-GUID-
0032, JCI, No. 5 at pp. 4-6)
Mortex also commented that replacement with a different evaporator
coil design and size could lead to issues of fitting or size constraint
problems and refrigerant metering and charging differences. The end
result (if design air volume rate is hampered and refrigerant circuit
performance is modified) could lead to less efficiency than the pre-
failure situation. (Docket No. EERE-2014-BT-GUID-0032, Mortex, No. 6 at
p. 1)
DOE also notes that the ASRAC regional standards enforcement
Working Group agreed that manufacturers do not need to keep track of
components including uncased coils. (Docket No. EERE-2011-BT-CE-0077-
0070, Attachment)
In consideration of the comments and the Working Group proposals,
DOE notes that its proposed definition of ``indoor unit'' refers to the
box rather than just a coil. Accordingly, legacy indoor coil
replacements and uncased coils would not meet the definition of indoor
unit. Furthermore, by defining air conditioners and heat pumps as
consisting of a single-package unit, an outdoor unit and one or more
indoor units, an indoor unit only, or an outdoor unit only, legacy
indoor coil replacements and uncased coils would not meet the
definition of a central air conditioner or heat pump. Hence, they would
not need to be tested or certified as meeting the standard.
g. Outdoor Units With No Match
For split-system central air conditioners and heat pumps, current
DOE regulations require that manufacturers test the condensing unit and
``the evaporator coil that is likely to have the largest volume of
retail sales with the particular model of condensing unit'' (commonly
referred to as the highest sales volume combination). 10 CFR
4429.16(a)(2)(ii). Effective January 1, 2010, the U.S. Environmental
Protection Agency (EPA) banned the sale and distribution of those
central air conditioning systems and heat pump systems that are
designed to use HCFC-22 refrigerant. 74 FR 66450 (Dec. 15, 2009). EPA's
rulemaking included an exception for the manufacture and importation of
replacement components, as long as those components are not pre-charged
with HCFC-22. Id. at 66459-60.
Because complete HCFC-22 systems can no longer be distributed,
manufacturers inquired how to test and rate individual components--
because these components are sold separately, there are no highest
sales volume combinations. Because the EPA prohibits distribution of
new HCFC-22 condensing unit and coil combinations (i.e., complete
systems), there is no such thing as a HSVC, and hence, testing and
rating of new HCFC-22 combinations cannot be conducted using the
existing test procedure.
DOE expects that the HCFC-22 indoor and outdoor units remaining on
the market are part of legacy offerings that were initially sold five
or more years ago. These components of HCFC-22 systems were in
production for sale as part of matched systems before the EPA
regulations became effective on January 1, 2010. While EPA's rulemaking
bans the sale of HCFC-22 systems that are charged with refrigerant
while allowing sale of uncharged components of such systems, EPA's rule
has no effect on the efficiency rating of these systems or on
requirements for DOE efficiency standards that they must meet. The DOE
test procedure used prior to January 15, 2010 that would have been used
to rate these systems is no longer valid, thus these ratings can no
longer be used as the basis for representing their efficiency. The
individual indoor coils and outdoor units of such systems that could
potentially meet the current standard may continue to be manufactured
only if the manufacturer uses a valid test procedure to ensure
compliance (i.e., to certify compliance) and for representations.
Generally, when a model cannot be tested in accordance with the DOE
test procedure, manufacturers must submit a petition for a test
procedure waiver for DOE to assign an alternative test method. 10 CFR
430.27(a)(1) Instead, DOE proposes in this notice a test procedure that
may be used for rating and certifying the compliance of these outdoor
units. DOE proposes in this notice to specify coil characteristics that
should be used when testing models of outdoor units that do not have a
HSVC. Specifically, these requirements include limitations on coil tube
geometries and dimensions and coil fin surface area. These outdoor unit
models, when tested with the specified indoor units, must meet
applicable Federal standards. (See section III.A.4 for more information
on compliance.) This proposal is consistent with the regional standards
enforcement Working Group recommendation that a person cannot install a
replacement outdoor unit unless it is certified as part of a
combination that meets the applicable standard. (Docket No. EERE-2011-
BT-CE-0077-0070, Attachment) The new test procedure would be effective
(i.e., allowed for use for such certifications) 30 days after it is
finalized and would be required for use for such systems (i.e., rather
than any granted waiver test procedure) beginning 180 days after it is
finalized.
In response to the August 20, 2014 draft guidance document, Carrier
requested clarification that the finalized guidance would replace DOE's
draft guidance document issued on January 1, 2012, regarding central
air conditioning systems and air conditioning heat pump systems that
are designed to use dry R-22 condensing units. (Docket No. EERE-2014-
BT-GUID-0032, Carrier, No. 7 at p. 2) If finalized, this proposed test
procedure would replace both the 2012 guidance document for dry R-22
units as well as the 2014 draft guidance document on unit selection
regarding condensing units for replacement applications.
4. Compliance With Federal (National or Regional) Standards
In the August 20, 2014 draft guidance document (EERE-2014-BT-GUID-
0032), DOE discussed whether each basic model of split-system air
conditioner or heat pump has to meet the applicable standard. DOE
stated that compliance with standards is based on the statistical
concept that an entire population of units (where ``unit'' refers to a
complete system) of a basic model must meet the standard, recognizing
that efficiency measurements for some units may be better or worse than
the standard due to manufacturing or testing variation. Manufacturers
apply the statistical formulae in 10 CFR 429.16 to demonstrate
compliance, and DOE applies the statistical formulae in 10 CFR part
429, subpart C, Appendix A to determine compliance.
Further, DOE stated that the only condensing units and coils that
may be installed in the region are those that can meet the regional
standard when tested and rated as a new system in accordance with the
test procedure and sampling plan as described above.
In response, AHRI and several manufacturers recommended the
following additions to DOE's statements regarding compliance:
``Compliance with national or regional standards is based on the
statistical concept that an entire population of units (where
``unit'' refers to a complete system) of a basic model including
Highest Sales Volume Tested Combination and all other combinations
must meet the standard, recognizing that some individual units may
perform slightly better or worse than the design due to
manufacturing or testing variation.''
(Docket No. EERE-2014-BT-GUID-0032, AHRI, No. 8 at p. 2; Rheem,
No. 2 at p. 2; Goodman, No. 10 at p. 2; Ingersoll Rand, No. 3 at p.
1; Lennox, No. 4 at p. 2; Nordyne, No.
[[Page 69290]]
9 at pp. 1-2; JCI, No. 5 at p. 3; Carrier, No. 7 at p. 6)
In addition, Carrier commented that with respect to the discussion
about selection of units for testing, the HSVC should be determined for
the applicable region. (Docket No. EERE-2014-BT-GUID-0032, Carrier, No.
7 at p. 4)
AHRI and several manufacturers recommended the following addition
to the paragraph on condensing units sold as replacements:
``In summary, DOE interprets for the regional standard to
require that the least efficient rating combination for a specified
model of condensing unit must be 14 SEER with a coil only rating
where 14 SEER is the regional standard. Any model that has a
certified combination below the regional standard cannot be
installed in the region. This interpretation of the regional
standard also applies to units shipped without refrigerant charge.''
(Docket No. EERE-2014-BT-GUID-0032, AHRI, No. 8 at p. 2; Rheem,
No. 2 at p. 3; Goodman, No. 10 at p. 3; Ingersoll Rand, No. 3 at p.
3; Lennox, No. 4 at p. 3; Nordyne, No. 9 at pp. 2-3; JCI, No. 5 at
p. 6)
Carrier provided slightly different recommended language:
``Given the different Federal standards, National and regional,
the least efficient rating combination for a specified model of
condensing unit must: (i) in the regions where the regional standard
applies, be rated and certified on as performing at or above the
current regional standard with a coil only rating; and (ii) where
the National standard applies, be rated and certified as performing
at or above the current National standard with a coil only rating.
For purposes of clarity, any basic model that has a certified
combination below the current regional standard cannot be installed
in the region. This interpretation also applies to dry condensing
units.'' (Docket No. EERE-2014-BT-GUID-0032, Carrier, No. 7 at pp.
1-2)
In contrast, Carrier also suggested that the guidance document
discussion of unit selection and basic models should replace references
to ``Federal standard'' with ``Federal (national or regional)
standard''. (Carrier, No. 7 at pp. 4-5)
The regional standards enforcement Working Group suggested the
regional standards required clarification because a particular
condensing unit may have a range of efficiency ratings when paired with
various indoor evaporator coils and/or blowers. The Working Group
provided the following four recommendations to clarify the regional
standards: That (1) the least-efficient rated combination for a
specified model of condensing unit must be 14 SEER for models installed
in the Southeast and Southwest regions; (2) the least-efficient rated
combination for a specified model of condensing unit must meet the
minimum EER for models installed in the Southwest region; (3) any
condensing unit model that has a certified combination that is below
the regional standard(s) cannot be installed in that region; and (4) a
condensing unit model certified below a regional standard by the
original equipment manufacturer cannot be installed in a region subject
to a regional standard(s) even with an independent coil manufacturer's
indoor coil or air handler combination that may have a certified rating
meeting the applicable regional standard(s). (Docket No. EERE-2011-BT-
CE-0077-0070, Attachment)
After reviewing stakeholder comments and the Working Group report,
DOE agrees that all individual models or combinations within a basic
model must meet the applicable national or regional standard. DOE
proposes to add requirements to the relevant provisions of section
430.32 that the least-efficient combination of each basic model must
comply with the regional SEER and EER standards.
In addition, as noted in section III.A.1, DOE proposes that if any
individual combination within a basic model fails to meet the standard,
the entire basic model (i.e., model of outdoor unit) must be removed
from the market. In order to clarify the limitations on sales of models
of outdoor units across regions with different standards, DOE proposes
to add a limitation in section 429.16 that any model of outdoor unit
that is certified in a combination that does not meet all regional
standards cannot also be certified in a combination that meets the
regional standard(s). Outdoor unit model numbers cannot span regions
unless the model of outdoor unit is compliant with all standards in all
possible combinations. If a model of outdoor unit is certified below a
regional standard, then it must have a unique individual model number
for distribution in each region. For example:
----------------------------------------------------------------------------------------------------------------
Individual model # Individual model # Certified rating
Basic model (outdoor unit) (indoor unit) (SEER/EER) Permitted?
----------------------------------------------------------------------------------------------------------------
AB12..................... ABC**#**-***........ SO123............... 14.5/12.0 NO.
AB12..................... ABC**#**-***........ SW123............... 15.0/12.8
AB12..................... ABC**#**-***........ N123................ 13.9/11.7
CD13..................... CDESO**-*#*......... SO123............... 14.5/12.0 YES.
CD13..................... CDESW**-*#*......... SW123............... 15.0/12.8
CD13..................... CDEN***-*#*......... N123................ 13.9/11.7
EF12..................... EFCS**#**-***....... SO123............... 14.5/12.2 YES.
EF12..................... EFCS**#**-***....... SW123............... 14.6/12.4
EF12..................... EFCN**#**-***....... N123................ 13.9/11.7
----------------------------------------------------------------------------------------------------------------
5. Certification Reports
To maximize test repeatability and reproducibility for assessment
and enforcement testing, DOE proposes to amend the certification
reporting requirements.
DOE proposes to clarify what basic model number and individual
model numbers must be reported for central air conditioners and heat
pumps:
----------------------------------------------------------------------------------------------------------------
Individual model number(s)
Equipment type Basic model number -----------------------------------------------------------
1 2 3
----------------------------------------------------------------------------------------------------------------
Single Package.................. Number unique to Package........... N/A............... N/A.
the basic model.
Split System (rated by OUM)..... Number unique to Outdoor Unit...... Indoor Unit(s).... Air Mover (or N/A
the basic model. if rating coil-
only system or
fan is part of
indoor unit model
number).
[[Page 69291]]
Outdoor Unit Only............... Number unique to Outdoor Unit...... N/A............... N/A.
the basic model.
Split-System or SDHV (rated by Number unique to Outdoor Unit...... Indoor Unit(s).... N/A.
ICM). the basic model.
----------------------------------------------------------------------------------------------------------------
Each basic model number must be unique in some way so that all
individual models or combinations within the same basic model can be
identified.
DOE also proposes to require product-specific information at 10 CFR
429.16(c)(4) that is not public and will not be displayed in DOE's
database. Several proposed requirements are addressed in the remainder
of this notice in response to comments on specific issues or in
relation to test procedure changes. In addition, several other
requirements are discussed in this section.
In order for DOE to replicate the test setup for its assessment
tests, DOE proposes that manufacturers that wish to certify multi-
split, multiple-circuit, and single-zone-multiple-coil systems report
the number of indoor units tested with the outdoor unit, the nominal
cooling capacity of each indoor unit and outdoor unit, and the indoor
units that are not providing heating or cooling for part-load tests.
Manufacturers that wish to certify systems that operate with multiple
indoor fans within a single indoor unit shall report the number of
indoor fans; the nominal cooling capacity of the indoor unit and
outdoor unit; which fan(s) are operating to attain the full-load air
volume rate when controls limit the simultaneous operation of all fans
within the single indoor unit; and the allocation of the full-load air
volume rate to each operational fan when different capacity blowers are
connected to the common duct.
Similarly, DOE proposes that for those models of indoor units
designed for both horizontal and vertical installation or for both up-
flow and down-flow vertical installations, the orientation used during
certification testing shall be included on the certification test
reports.
DOE also proposes that the maximum time between defrosts as allowed
by the controls be included on the certification test reports. For
units with time-adaptive defrost control, the frosting interval used
during the Frost Accumulation tests and the associated procedure for
manually initiating defrost at the specified time, if applicable,
should also be included on the certification test reports.
DOE also proposes that for variable-speed units, the compressor
frequency set points and the required dip switch/control settings for
step or variable components should be included. For variable-speed heat
pumps, DOE proposes that manufacturers report whether the unit controls
restrict use of minimum compressor speed operation for some range of
operating ambient conditions, whether the unit controls restrict use of
maximum compressor speed operation for any ambient temperatures below
17 [deg]F, and whether the optional H42 low temperature test
was used to characterize performance at temperatures below 17 [deg]F.
Finally, DOE proposes that manufactures report air volume rates and
airflow-control settings.
DOE recognizes that additional reporting requirements in
certification test reports increases reporting burden because
manufacturers must spend additional time to add such content to the
report. However, DOE believes that a knowledgeable person in the field
would not find the additional information difficult to provide and
could do so in a reasonable amount of time. Thus, DOE does not believe
that the added reporting requirements are significantly burdensome to
warrant excluding them. DOE requests comment on this issue.
6. Represented Values
DOE proposes to make several additions to the represented value
requirements in 10 CFR 429.16. First, DOE proposes to add a requirement
that the represented value of cooling capacity, heating capacity, and
sensible heat ratio (SHR) shall be the mean of the values measured for
the sample. Second, DOE proposes to move the provisions currently in 10
CFR 430.23 regarding calculations of various measures of energy
efficiency and consumption for central air conditioners to 10 CFR
429.16. Specifically, while Part 430 would refer to the test procedure
appendix and section therein to use for each metric and the rounding
requirements for test results of individual units, Part 429 would refer
to how to calculate annual operating cost for the sample based on
represented values of cooling capacity and SEER, and how to round the
represented values based on the sample for other measures of energy
efficiency and consumption. DOE proposes minor changes to the
calculations of annual operating cost to address changes proposed in
Appendix M and M1. Table III.3 shows the proposed rounding requirements
for each section. DOE requests comment on these values.
Table III.3--Rounding Proposals
------------------------------------------------------------------------
10 CFR 430.23 (one 10 CFR 429.16
Measure unit) (sample)
------------------------------------------------------------------------
Cooling capacity/heating
capacity:
<20,000 Btu/h............... nearest 50 Btu/h.. nearest 100 Btu/h.
>=20,000 Btu/h and <38,000 nearest 100 Btu/h. nearest 200 Btu/h.
Btu/h.
>=38,000 Btu/h and <65,000 nearest 250 Btu/h. nearest 500 Btu/h
Btu/h.
Annual operating cost........... N/A............... nearest dollar per
year.
EER/SEER/HSPF/APF............... nearest 0.025..... nearest 0.05.
Off-mode power consumption...... nearest 0.5 watt.. nearest watt.
Sensible heat ratio............. nearest 0.5%...... nearest percent
(%).
------------------------------------------------------------------------
[[Page 69292]]
7. Product-Specific Enforcement Provisions
DOE proposes to verify during assessment or enforcement testing the
cooling capacity certified for each basic model or individual
combination. DOE proposes to measure the cooling capacity of each
tested unit pursuant to the test requirements of 10 CFR part 430. The
results of the measurement(s) will be compared to the value of cooling
capacity certified by the manufacturer. If the measurement is within
five percent of the certified cooling capacity, DOE will use the
certified cooling capacity as the basis for determining SEER.
Otherwise, DOE will use the measured cooling capacity as the basis for
determining SEER.
DOE also proposes to require manufacturers to report the cyclic
degradation coefficient (CD) value used to determine
efficiency ratings. In this proposal, DOE would run CD
testing as part of any assessment or verification testing, except when
testing an outdoor unit with no match. If the measurement is 0.02 or
more greater than the certified value, DOE would use the measurement as
the basis for calculation of SEER or HSPF. Otherwise, DOE would use the
certified value. For models of outdoor units with no match, DOE would
always use the default value.
B. Alternative Efficiency Determination Methods
1. General Background
For certain consumer products and commercial equipment, DOE's
existing regulations allow the use of an alternative efficiency
determination method (AEDM) or alternative rating method (ARM), in lieu
of actual testing, to estimate the ratings of energy consumption or
efficiency of basic models by simulating their energy consumption or
efficiency at the test conditions required by the applicable DOE test
procedure. The simulation method permitted by DOE for use in rating
split-system central air conditioners and heat pumps, in accordance
with 10 CFR 429.70(e), is referred to as an ARM. In contrast to an
AEDM, an ARM must be approved by DOE prior to its use.
The simulation methods represented by AEDMs or ARMs are computer
modeling or mathematical tools that predict the performance of non-
tested individual or basic models. They are derived from mathematical
models and engineering principles that govern the energy efficiency and
energy consumption of a particular basic model of covered product based
on its design characteristics. (In the context of this discussion, the
term ``covered product'' applies both to consumer products and
commercial and industrial equipment that are covered under EPCA.) These
computer modeling and mathematical tools can provide a relatively
straightforward means to predict the energy usage or efficiency
characteristics of an individual or basic model of a given covered
product and reduce the burden and cost associated with testing certain
covered products that are inherently difficult or expensive to test.
When properly developed, they can predict the performance of a product
accurately enough to be statistically representative under DOE's
sampling requirements.
On April 18, 2011, DOE published a Request for Information (AEDM
RFI) in the Federal Register. 76 FR 21673. Through the AEDM RFI, DOE
requested suggestions, comments, and information relating to the
Department's intent to expand and revise its existing AEDM and ARM
requirements for consumer products and commercial and industrial
equipment covered under EPCA. In response to comments it received on
the AEDM RFI, DOE published a Notice of Proposed Rulemaking (AEDM NOPR)
in the Federal Register on May 31, 2012. 77 FR 32038. DOE also held a
public meeting on June 5, 2012, to present proposals in the AEDM NOPR
and to receive comments from stakeholders. In the AEDM NOPR, DOE
proposed the elimination of ARMs, and the expansion of AEDM
applicability to those products for which DOE allowed the use of an ARM
(i.e., split-system central air conditioners and heat pumps). 77 FR at
32055. Furthermore, DOE proposed a number of requirements that
manufacturers must meet in order to use an AEDM as well as a method
that DOE would employ to determine if an AEDM was used appropriately
along with specific consequences for misuse of an AEDM. 77 FR at 32055-
56.
The purpose of the AEDM rulemaking was to establish a uniform,
systematic, and fair approach to the use of modeling techniques that
would enable DOE to ensure that products in the marketplace are
correctly rated--irrespective of whether they are rated based on
physical testing or modeling--without unnecessarily burdening regulated
entities. DOE solicited suggestions, comments, and information related
to its proposal and accepted written comments on the AEDM NOPR through
July 2, 2012. DOE subsequently formed a working group through the
Appliance Standards and Rulemaking Federal Advisory Committee (ASRAC)
(see the Notice of Intent To Form the Commercial HVAC, WH, and
Refrigeration Certification Working Group and Solicit Nominations To
Negotiate Commercial Certification Requirements for Commercial HVAC,
WH, and Refrigeration Equipment, published on March, 12, 2013, 78 FR
15653), which addressed revisions to the AEDM requirements for
commercial and industrial equipment covered by EPCA and resulted in the
subsequent publishing of a SNOPR on October 22, 2013 (78 FR 62472) and
a final rule on December 31, 2013 (78 FR 79579). In the final rule, DOE
made, among others changes, revisions to pre-approval requirements,
validation requirements, and DOE verification testing requirements for
the AEDM process for commercial HVAC equipment.
In this notice, DOE proposes modifications to the central air
conditioners and heat pump AEDM requirements proposed in the AEDM NOPR
with consideration of the comments received on the AEDM NOPR specific
to these products, as well as the requirements implemented for
commercial HVAC equipment in the December 2013 AEDM final rule.
2. Terminology
In the AEDM NOPR, DOE proposed to eliminate the term ``alternate
rating method'' (ARM) and instead use the term ``alternative efficiency
determination method'' (AEDM) to refer to any modeling technique used
to rate and certify covered products. 77 FR 32038, 32040 (May 31,
2012). DOE proposed to refer to any technique used to model product
performance as an AEDM, but recognized that there are product-specific
considerations that should be accounted for in the development of an
AEDM and thus, in the proposed methodology for validating product-
specific AEDMs. Id.
DOE received a number of comments in response to its proposal to
solely apply the term AEDM to any modeling technique used to rate and
certify covered products. Bradford White Corporation (Bradford White),
United Technologies Climate, Controls & Security and ITS Carrier (UTC/
Carrier), and Nordyne, LLC (Nordyne) agreed with DOE that one term
should be used. (Docket No. EERE-2011-BT-TP-0024, Bradford White, No.
38 at p. 1; UTC/Carrier, No. 56 at p. 1; Nordyne, No. 55 at p. 1) \8\
AAON, Inc. (AAON) supported
[[Page 69293]]
DOE's proposal to combine requirements for ARMs and AEDMs, but did not
differentiate between the terminology and the methodological changes
proposed. (AAON, No. 40 at p. 2) DOE also received a number of
comments, both written and at the public meeting, regarding the
differences in ARM and AEDM methodology. Those comments are discussed
in section III.B.3 of this document. In addition, DOE received numerous
comments regarding the validation of AEDMs for different product types,
which are discussed in section III.B.4 of this document.
---------------------------------------------------------------------------
\8\ Unless otherwise specified, further references in this
section (section III.B) to comments received by DOE are to those
associated with the AEDM rulemaking (Docket No. EERE-2011-BT-TP-
0024). References to the public meeting are to the June 5, 2012
public meeting on the AEDM NOPR, the transcript of which is in the
AEDM rulemaking docket.
---------------------------------------------------------------------------
In response to comments received, DOE is continuing to propose the
use of one term, AEDM, to refer to all modeling techniques used to
develop certified ratings of covered products. DOE believes that since
the two methods are conceptually similar, the use of one term is
appropriate. DOE would like to clarify that the use of one term to
refer to all modeling techniques used to develop certified ratings of
covered products and equipment does not indicate a uniform process or
requirements for their use across all covered products, nor does it
imply that DOE will not include any of the current ARM provisions as
part of the proposed AEDM provisions. Further, similar to the
differences between AEDMs for distribution transformers and commercial
HVAC products, DOE proposes validation requirements that will account
for the differences between HVAC products and other covered equipment.
3. Elimination of the Pre-Approval Requirement
Under current regulations, ARMs used by manufacturers of split-
system central air conditioners and central heat pumps must be approved
by the Department before use. (10 CFR 429.70(e)(2)) Manufacturers who
elect to use an ARM to rate untested basic models pursuant to 10 CFR
429.16(a)(2)(ii)(B)(1) must, among other requirements, submit to the
Department full documentation of the rating method including a
description of the methodology, complete test data on four mixed
systems per each ARM, and product information on each indoor and
outdoor unit of those systems. Furthermore, manufacturers are not
permitted to use the ARM as a rating tool prior to receiving
Departmental approval.
In the AEDM RFI, DOE requested comment on the necessity of a pre-
approval requirement for AEDMs and/or ARMs. 76 FR 21673, 21674 (April
18, 2011). Based on the comments received in response to the AEDM RFI,
DOE perceived no benefit in the additional burden imposed by a pre-
approval requirement and that a pre-approval process could cause time-
to-market delays. Pursuant to those comments, DOE proposed in the AEDM
NOPR to eliminate the pre-approval process currently in place for
central air conditioner and heat pump ARMs. 77 FR 32038, 32040-41 (May
31, 2012). DOE believed that this would reduce the burden currently
placed on manufacturers by eliminating the time-to-market delays caused
by completing the necessary request for approval before bringing
products to market. Furthermore, DOE believed that elimination of the
pre-approval requirement would promote innovation because an ARM would
not need to be approved or re-approved to account for any changes in
technology. Id.
In the AEDM NOPR, DOE sought comment regarding its proposal to
eliminate the pre-approval requirement for ARMs for central air
conditioners and heat pumps and received mixed responses. Modine
Manufacturing Corporation (Modine) supported DOE's proposal to
eliminate the pre-approval requirement. (Modine, No. 42 at p. 1) Lennox
International, Inc. (Lennox) and Unico, Inc. (Unico), however,
suggested that removal of the pre-approval requirement could lead to
incorrect ratings and unfair competition in the marketplace, which
could negatively impact consumers. (Lennox, No. 46 at p. 2; Unico, No.
54 at p. 2) Furthermore, Johnson Controls, Inc. (JCI) commented that it
was particularly important that manufacturers continue to be allowed to
use pre-approved ARMs because the new AEDM provisions, by eliminating
pre-approval, introduce regulatory risk that is not present under
current ARM requirements. (JCI, No. 66 at pp. 2)
Other interested parties specifically recommended that
participation in a voluntary industry certification program (VICP),\9\
or review of an AEDM or ARM by a qualified engineer, could reduce or
eliminate the need for pre-approval. AHRI, Rheem Manufacturing Company
(Rheem), Goodman Global, Inc. (Goodman), and Unico suggested that DOE
should consider pre-approval for manufacturers not participating in a
VICP, and that at a minimum, review by a professional engineer should
be required. (AHRI, No. 61 at p. 2; Rheem, No. 59 at p. 2; Goodman, No.
53 at p. 1; Unico, No. 54 at p. 5) Likewise, Lennox agreed that if DOE
does not maintain pre-approval in general, it could still require pre-
approval for those who do not participate in a VICP . (Lennox, No. 46
at pp. 2 and 4) Lennox and Rheem commented that a pre-approval
requirement for manufacturers who do not participate in a VICP could
protect consumers from unsubstantiated ratings. (Rheem, No. 59 at p. 2;
Lennox, No. 46 at p. 2)
---------------------------------------------------------------------------
\9\ A Voluntary Industry Certification Program, or VICP, is an
independent, third-party program that conducts ongoing verification
testing of members' products.
---------------------------------------------------------------------------
DOE does not agree with JCI's suggestion that the elimination of
pre-approval could create additional burden for manufacturers in cases
where they fail to meet certified ratings and are subsequently required
to re-substantiate their AEDM. DOE also does not agree with Rheem
Lennox, and Unico who claim that the elimination of pre-approval will
lead to incorrect ratings in the marketplace or create unfair
competition. Pre-approval of an ARM that is used to certify a basic
model rating does not mean that the basic model is correctly rated.
Products that are certified using an approved ARM are subject to the
same assessment testing and enforcement actions as those products
certified through testing and/or use of an AEDM. Further, DOE currently
has the authority to review approved ARMs at any time, including review
of documentation of tests used to support the ARM. DOE may also test
products that were certified using an ARM to determine compliance with
the applicable sampling provisions, as well as with federal standards.
Should DOE determine that products were incorrectly rated, DOE may
require that the ARM is no longer used. Similarly, AEDMs used to
certify ratings are subject to review at any time, as well as the
potential for suspension should DOE determine that products were
incorrectly rated. Additionally, as discussed in section III.A.3.a,
each basic model must have at least one rating determined through
testing; no basic model can be rated solely using an AEDM, which
reduces the likelihood of significant error. Finally, use of a pre-
approved ARM does not insulate a manufacturer from responsibility for
the accuracy of their ratings, and the misconception that it does
presents another reason to eliminate DOE review. Most manufacturers
have not updated their ARMs and submitted the revised ARM for DOE
review as required by regulation since prior to the last standards
update and, thus, are effectively using unapproved or outdated ARMs
currently. For these reasons, it is DOE's view that the elimination of
the pre-approval process would not have a substantive
[[Page 69294]]
detrimental effect on the accuracy of a manufacturer's ratings, will
improve manufacturers' ability to introduce new products into the
marketplace, and will not represent a significant change from the
status quo.
For the forgoing reasons, in this SNOPR, DOE proposes to eliminate
the pre-approval process for ARMs for split-system central air
conditioners and heat pumps. As stated in the AEDM NOPR, DOE believes
that this will reduce time-to-market delays, facilitate innovation, and
eliminate the time required to complete the approval process.
Furthermore, DOE emphasizes that the Department's treatment of products
that are currently rated and certified with the use of an ARM does not
differ from its treatment of products currently rated and certified
using an AEDM, except for the pre-approval requirement. (See for
example 10 CFR 429.70(c).)
In addition, DOE proposes that manufacturers may only apply an AEDM
if it (1) is derived from a mathematical model that estimates
performance as measured by the applicable DOE test procedure; and (2)
has been validated with individual combinations that meet current
Federal energy conservation standards (as discussed in the next
section). Furthermore, DOE proposes records retention requirements and
additional manufacturer requirements to permit DOE to audit AEDMs
through simulations, review of data and analyses, and/or certification
testing.
4. AEDM Validation
In the AEDM NOPR, DOE proposed product-specific AEDM validation
requirements meant to reduce confusion and allow for easier development
and utilization of AEDMs by manufacturers. 77 FR 32044-32045. The
proposed validation requirements applicable to central air conditioner
and heat pump products would have required manufacturers to:
a. Test a minimum of five basic models, including at least one
basic model from each product class to which the AEDM would be applied.
b. Test the smallest and largest capacity basic models from the
product class with the highest sales volume.
c. Test the basic model with the highest sales volume from the
previous year, or the basic model which is expected to have the highest
sales volume for newly introduced basic models.
d. Validate only with test data that meets applicable Federal
energy conservation standards and was derived using applicable DOE
testing procedures.
In response to these proposed validation requirements, DOE received
a number of comments from stakeholders addressing specific products
covered by the AEDM rule. Comments applicable to the proposed
requirements for central air conditioner and heat pump products are
discussed in the following sections.
a. Number of Basic Models From a Product Class Necessary To Validate an
AEDM
Commenter responses with regard to the minimum sample size of one
unit each of five different basic models were mixed, with some
commenters agreeing with DOE's proposal and some offering alternative
sample sizes. Both AAON and Goodman agreed with DOE's proposal that a
minimum of one unit each of five basic models be tested to validate the
AEDM. (AAON, No. 40 at p. 6; Goodman, No. 53 at p. 2) AHRI, however,
commented that it was not realistic for a manufacturer who produces two
basic models, for example, to be required to validate an AEDM based on
a minimum sample of five units of the same two basic models. (AHRI,
Public Meeting Transcript, No. 69 at p. 154) Furthermore, AHRI stated
that it is disproportionately burdensome to require testing of at least
five basic models for small manufacturers who manufacture or wish to
use an AEDM for only a few basic models compared to manufacturers who
offer many basic models and many product classes. AHRI recommended that
DOE require testing of only 3 basic models if the AEDM is to be applied
to 15 or fewer basic models. (AHRI No. 61 at p. 3) United Cool Air
agreed with AHRI's concerns and stated that to obtain data that are
statistically robust enough to meet the validation requirements,
testing of at least two to five units of many basic models would be
necessary, which may be too burdensome for built-to-order and small
manufacturers. This would be particularly burdensome in cases where
models used for testing cannot be sold. (United Cool Air, No. 51 at pp.
7, 10, and 11) Acknowledging the amount of work and complex testing
required for validation of an AEDM, Zero Zone, Inc. (Zero Zone) noted
that it would be difficult for small manufacturers to comply. Zero Zone
recommended that small manufacturers could be exempt or have a
different sample size requirement. (Zero Zone, Public Meeting
Transcript, No. 69 at p. 65)
Other stakeholders commented on the validation requirements for
specific products. JCI stated that testing of five units is
unnecessarily burdensome and suggested that testing a minimum of three
units would be sufficient to validate HVAC AEDMs. (JCI, No. 66 at p. 6)
First Co. stated that DOE's proposed requirements would unreasonably
burden small manufacturers, especially independent coil manufacturers
because they would not have knowledge of which condensing unit model is
expected to have the highest sales volume in the coming year. First Co.
stated that this proposed requirement is unnecessary and should be
eliminated given that the proposed validation requirements already
include testing of the smallest and largest capacity basic model from
the product class with the highest sales volume, and that the current
minimum number of tests required for obtaining ARM approval is four.
(First Co., No. 45 at p. 2) JCI agreed with First Co., stating that the
proposal would create an overrepresentation of the highest sales volume
product class because the highest sales volume basic model is most
likely from that product class, and along with the requirement to test
the smallest and largest capacity basic model from that product class,
would require testing of three basic models from the highest sales
volume product class. (JCI, No. 66 at p. 7) Goodman, on the other hand,
stated that an additional test beyond the currently required four tests
would not cause significant burden. (Goodman, No. 53 at p. 2)
DOE notes that in its proposed revisions to the determination of
certified ratings for central air conditioners and heat pumps
(discussed in section III.A.3), manufacturers must test each basic
model; specifically for split-system air conditioners and heat pumps,
OUMs must test each model of outdoor unit with at least one model of
indoor unit (highest sales volume), and ICMs must test each model of
indoor unit with at least one model of outdoor unit (lowest SEER).
Manufacturers would only be able to use AEDMs for other individual
combinations within the same basic model--in other words, other
combinations of models of indoor units with the same model of outdoor
unit. DOE does not seek to require additional testing to validate an
AEDM beyond what is proposed under 10 CFR 429.16(a)(1)(ii). Therefore,
the testing burden required to validate an AEDM would depend on the
number of basic models each manufacturer must rate. Furthermore,
because ICMs must test each model of indoor unit with the lowest-SEER
model of outdoor unit with which it is paired, First Co.'s concerns
related to predicting the highest sales volume model would no longer be
relevant. DOE requests comment on its proposal related to the testing
[[Page 69295]]
requirements for validation of an AEDM.
Regarding the proposed requirement to test a basic model from each
applicable product class for HVAC products, Goodman believes that the
current definition of ``product class'' does not address the specific
issues raised by split-system central air conditioners and heat pumps,
which consist of separate indoor and outdoor coils that only function
as intended when paired with one another to form a unitary split-system
central air conditioner or heat pump. Hence, Goodman suggested that DOE
consider the following product types to constitute individual
validation classes: Split-system air conditioners, split-system heat
pumps, single-package air conditioners, and single-package heat pumps.
(Goodman, No. 53 at p. 4) UTC/Carrier proposed separate validation
classes for the categories mentioned by Goodman, but also proposed that
central air conditioners and heat pumps should include distinct
validation classes for space-constrained air conditioners and space-
constrained heat pumps. (UTC/Carrier, No. 56 at p. 2) United Cool Air
stated that DOE did not properly address classification of space-
constrained HVAC systems. (United Cool Air, No. 51 at p. 4, 13) United
Cool Air's comments align with comments from Carrier that DOE should
create a separate product class for space-constrained equipment.
In response, DOE notes that the proposed testing requirements in
429.16 require testing at least one individual model/combination within
each basic model. Therefore, by default manufacturers would be testing
all basic models from each product class in which they manufacture
units.
b. Selection of Capacity Variations of a Basic Model for Validating an
AEDM
Regarding selection of basic models for validating an AEDM, both
Nordyne and Goodman agreed with DOE's proposal that the basic models
selected for validating an AEDM must include the smallest capacity
basic model as well as the largest capacity basic model (or a basic
model within 25 percent of the largest capacity). (Nordyne, No. 55 at
p. 2; Goodman, No. 53 at p. 2) Rheem, however, disagreed and stated
that the requirement to test the smallest and largest capacity basic
model was too restrictive and does not account for outliers or
differences in technology across product classes. (Rheem, No. 59 at p.
4) Furthermore, Lennox noted that the manufacturer is most suited to
determine which models should be used for validation and that
requirements for particular capacities do not account for variation in
product design and construction. (Lennox, No. 46 at p. 4)
DOE's intention when proposing to require that a manufacturer test
both the smallest and largest capacity basic models within the product
class with the highest sales volume was to ensure that the AEDM could
accurately predict the efficiency of those products at the extremes of
a manufacturer's product line. As variations in product design and
construction across all capacities should be accounted for when testing
all basic models, DOE withdraws the proposal regarding selecting the
smallest and largest capacity basic models from the product class with
the highest sales volume for testing for validation of the AEDM. DOE
notes that in the proposed revisions to the determination of certified
ratings, each basic model must be tested and an AEDM can only be used
to certify other individual combinations that are part of the same
basic model.
c. Use of the Highest Sales Volume Basic Model for Validating an AEDM
Many interested parties recommended that DOE continue to require
that split-system manufacturers test each condensing unit they
manufacture with the evaporator coil that is likely to have the largest
volume of retail sales (i.e., the highest sales volume combination, or
HSVC) because the data resulting from these test combinations are
critical to independent coil manufacturers (ICMs) in determining
accurate ratings for their products since they must determine their
ratings based on pairings with condensing units offered by other
manufacturers. AHRI stated that DOE should retain requirements for
testing based on the HSVC for central air conditioners and heat pumps.
(AHRI, No. 61 at p. 2) UTC/Carrier agreed that DOE should allow split-
systems to retain the HSVC process, as is required by current ARM
regulations. (UTC/Carrier, No. 56 at p. 1) Lennox disagreed with
removing the requirement for testing based on HSVC because the current
AHRI certification program and independent coil manufacturing industry
depend on this requirement, and the data from HSVC test results are
used by independent coil manufacturers (ICMs) as the input to their
ARM. (Lennox, No. 46 at p. 4)
Unico stated that DOE should maintain the current ARM requirements
for central air conditioners and heat pumps because as an indoor coil
manufacturer, Unico relies on the accuracy of the ratings published by
the manufacturer of the outdoor unit and decreasing the accuracy of
those ratings would increase their own risk of failure. Unico stressed
that it was particularly important for DOE to allow manufacturers'
rating methodology to rely on curve fit data, and specifically proposed
that for validating an AEDM, matched system manufacturers should test
at least the highest sales volume combination for each outdoor unit.
(Unico, No. 54 at pp. 2, 4, and 6) Mortex Products, Inc. (Mortex)
stated that in order for ICMs to rate indoor coils accurately using the
ARM, the system manufacturer's HSVC data is necessary, and if HSVC data
were no longer obtained from tests, but generated using an AEDM, the
accuracy of the indoor coil ratings would be affected. (Mortex, No. 58
at p. 1)
DOE recognizes the concerns of stakeholders who commented that
eliminating the requirement to test the HSVC for split-system products
could increase the burden on ICMs. DOE does not intend to eliminate
that requirement and notes that such requirement is proposed to be
retained in this notice, as discussed in section III.A.3.a. However,
DOE also proposes additional requirements for ICMs that are discussed
in section III.B.5. DOE also notes that the ARM provisions in the
current regulations do not clearly apply to ICMs, and most ICMs do not
have DOE-approved ARMs.
DOE's proposal in the AEDM NOPR required re-validation when the
HSVC changes. In response, Goodman stated that for split-system CACs
and HPs, testing the highest or expected highest sales volume
combination basic model would be appropriate as long as DOE does not
require re-validation of the AEDM if another basic model subsequently
becomes the highest sales volume combination. Determination of the
highest volume basic model should be based on sales data of the prior
year, or sales data or forecasts of the year of the AEDM's validation.
(Goodman, No. 53 at p. 3) United Cool Air was also concerned that
additional testing would be required if the highest selling basic model
changed. (United Cool Air, No. 51 at p. 9)
In response to the concerns of Goodman and United Cool Air
regarding re-validation if the HSVC changed, DOE agrees that re-
validation should not be required if test data used to validate the
AEDM was based on an expected HSVC that subsequently becomes a lower
sales volume model and is not proposing such a requirement in this
notice. DOE agrees with Goodman that determination of the highest
volume basic model should be based on sales data of the prior year,
sales data or forecasts of the year of the AEDM's
[[Page 69296]]
validation, or other similar information. Selection of the highest
volume basic model should reflect a good faith effort by the
manufacturer to predict the combination most likely to result in the
highest volume of sales. DOE notes that it may verify compliance with
this HSVC testing requirement.
d. Requirements for Test Data Used for Validation
In AEDM NOPR, DOE did not propose requirements on the test data
used for validation of an AEDM because any non-testing approaches to
certifying central air conditioners and heat pumps via an ARM were to
be approved by DOE prior to use. 77 FR 32043. However, if DOE adopts
the current proposal to remove the pre-approval requirement, certified
ratings generated using an AEDM would be unreliable without other
requirements to validate the AEDM against actual test data. Therefore,
DOE proposes in this notice to adopt requirements on test data similar
to those used for validation for commercial HVAC and water heating
equipment, as published in the AEDM final rule 78 FR 79579, 79584 (Dec.
31, 2013). Specifically, (1) for energy-efficiency metrics, the
predicted efficiency using the AEDM may not be more than 3 percent
greater than that determined through testing; (2) for energy
consumption metrics, the predicted efficiency using the AEDM may not be
more than 3 percent less than that determined through testing; and (3)
the predicted efficiency or consumption for each individual combination
calculated using the AEDM must comply with the applicable Federal
energy conservation standard. Furthermore, the test results used to
validate the AEDM must meet or exceed the applicable Federal standards,
and the test must have been performed in accordance with the applicable
DOE test procedure. If DOE has ordered the use of an alternative test
method for a particular basic model through the issuance of a waiver,
that is the applicable test procedure.
DOE proposes a validation tolerance of 3 percent because the
variability in a manufacturer's lab and within a basic model should be
more limited than lab-to-lab variability. DOE proposes tolerances for
verification testing of 5 percent to account for added lab-to-lab
variability.
5. Requirements for Independent Coil Manufacturers
In the AEDM NOPR, DOE did not propose a statistical sampling
requirement for independent coil manufacturers (ICMs) that would be
distinct from the sampling required to validate an AEDM for HVAC
products. 77 FR at 32043. In response, Unico commented that ICMs should
test coils of each fin-pattern, varying the number of rows, fin
density, tube type, circuiting, and frontal area. (Unico, No. 54 at p.
4) Mortex stated that their ARMs are based on data from a ``matched
system'' tested by an OUM. Mortex uses an ARM to simulate the
performance of their own coil in a matched system by substituting the
geometry of the indoor evaporator coil used by the manufacturer of the
condensing unit with the geometry of their own coil. (Mortex, No. 58 at
p. 1)
While DOE understands that ICMs currently use ratings from OUMs to
predict the efficiency of their coil models, as discussed in section
III.A.3.d, DOE is now proposing to require that ICMs test each of model
of indoor units (i.e., basic models) with the least efficient model of
outdoor unit with which it will be paired. In order to validate an AEDM
for split-systems rated by ICMs for other individual combinations
within each basic model, DOE also proposes that ICMs must use the
individual combinations the ICMs would be required to test under the
proposed text in 10 CFR 429.16. DOE seeks comment on this proposal.
In regard to Unico's suggestion to test indoor units with coils of
varying fin-patterns, DOE refers stakeholders to the definition of a
basic model in section III.A.1, and particularly what constitutes the
same model of indoor unit. DOE notes that the manner in which
manufacturers apply the basic model provisions would impact what models
of indoor units are required for testing.
6. AEDM Verification Testing
DOE may randomly select and test a single unit of a basic model
pursuant to 10 CFR 429.104. This authority extends to all DOE covered
products, including those certified using an AEDM. In the AEDM NOPR,
DOE clarified that a selected unit would be tested using the applicable
DOE test procedure at an independent, third-party laboratory accredited
to the International Organization for Standardization (ISO)/
International Electrotechnical Commission (IEC), ``General requirements
for the competence of testing and calibration laboratories,'' ISO/IEC
17025:2005E. 77 FR 32038, 32057 (May 31, 2012).
In this notice, DOE proposes further verification testing methods.
Specifically, DOE proposes that verification testing conducted by the
DOE will be (1) on a retail unit or a unit provided by the manufacturer
if a retail unit is not available, (2) at an independent, third-party
testing facility or a manufacturer's facility upon DOE's request if the
former is not capable of testing such a unit, and (3) conducted with no
communication between the lab and the manufacturer without DOE
authorization.
DOE also proposes clarification of requirements for determining
that a model does not meet its certified rating, as proposed in the
AEDM NOPR. Specifically, DOE proposes that an individual combination
would be considered as having not met its certified rating if, even
after applying the five percent tolerance between the test results and
the rating as specified in the proposed 10 CFR 429.70(e)(5)(vi), the
test results indicate the individual combination being tested is less
efficient or consumes more energy than indicated by its certified
rating. DOE notes that this approach will not penalize manufacturers
for applying conservative ratings to their products. That is, if the
test results indicate that the individual combination being tested is
more efficient or consumes less energy than indicated by its certified
rating, DOE would consider that individual combination to meet its
certified rating. DOE seeks comment on whether this is a reasonable
approach to identify an individual combination's failure to meet its
certified rating.
In the AEDM NOPR, DOE also proposed the actions DOE would take in
response to individual models that fail to meet their certified
ratings. 77 FR at 32056. Many stakeholders submitted comments
suggesting that DOE should determine the cause of the test failure
prior to taking any additional action. UTC/Carrier commented that
failure of a single unit test result could be a result of a defective
unit and further urged DOE to define a process to contest test results
from a third party lab. (UTC/Carrier, No. 56 at p. 2) JCI had a similar
concern regarding potential errors in test set-up and proposed that DOE
should work with the manufacturer to determine the root cause of the
failure, performing additional testing if necessary. (JCI, No. 66 at p.
8) Rheem agreed with JCI that DOE should work with the manufacturer to
determine whether the root cause is associated with test variability,
AEDM model inaccuracy, or manufacturing variability. Rheem added that
DOE should clarify what constitutes a ``failure'' as well as develop a
detailed plan for selection, testing, evaluation, manufacturer
notification, and resolution. (Rheem, No. 59 at p. 4) Lennox also
agreed that DOE should not immediately require modification of an
[[Page 69297]]
AEDM without first finding the cause of the failure. (Lennox, No. 46 at
pp. 4-5) Additionally, Ingersoll Rand requested that DOE allow for a
dialogue with the manufacturer to ensure that the sample unit was not
defective and that the test was set up correctly. (Ingersoll Rand,
Public Meeting Transcript, No. 69 at p. 187) AHRI agreed that it would
be valuable to specify particular steps manufacturers and DOE must take
in the case of a test failure and incorporate a defective sample
provision, and recommended that DOE provide data, a failure report, and
other necessary information to the manufacturer for proper analysis of
the test failure. (AHRI, No. 61 at pp. 6-7)
Unico and manufacturers of products other than HVAC suggested that
DOE should not only share the data with the manufacturer, but also
allow the manufacturer to review or witness testing done by a lab. This
would allow for better understanding of potential discrepancies in test
results and ensure that failure was not merely a result of variation in
test set-up. (Unico, No. 54 at p. 4) AHRI and UTC/Carrier suggested
that manufacturers should be allowed to participate in commissioning of
their equipment prior to the assessment test since proper set-up is
critical. AHRI added that manufacturers should have an opportunity to
repair a unit, if defective, while it is in the assessment lab. (AHRI,
No. 61 at pp. 6-7; Carrier, Public Meeting Transcript, No. 69 at p.
218) Further, UTC/Carrier urged DOE to specify an appeals process for
tests that a manufacturer believes were tested with improper test set-
up. (UTC/Carrier, Public Meeting Transcript, No. 69 at p. 195; UTC/
Carrier, No. 56 at p. 3)
DOE agrees that determining the root cause of the failure to meet
certified ratings is important; however, DOE stresses that this would
be the manufacturer's responsibility. DOE is aware that in order to
determine the cause of the failure, the manufacturer will need to
review the data from DOE's testing. DOE therefore proposes that when an
individual combination fails to meet certified ratings, DOE will
provide to the manufacturer a test report that includes a description
of test set-up, test conditions, and test results. DOE will provide the
manufacturer with an opportunity to respond to the lab report by
presenting all claims regarding testing validity, and if the
manufacturer was not on-site for initial set-up, to purchase an
additional unit from retail to test following the requirements in
429.110(a)(3). This process is designed to provide manufacturers the
opportunity to raise concerns about the test set-up, taking into
account various comments from stakeholders. DOE will consider any
response offered by the manufacturer within a designated time frame
before deciding upon the validity of the test results. Only after
following these steps will the Department make a determination that the
rating for the basic model is invalid and require the manufacturer to
take subsequent action, as described in section III.B.7.
7. Failure To Meet Certified Ratings
In the AEDM NOPR, DOE proposed a method of determining whether a
model meets its certified rating whereby the assessment test result
would be compared to the certified rating for that model. If the test
result was not within the tolerance in the proposed section 429.70(c),
the model would be considered as having not met its certified rating.
In this case DOE proposed to require that manufacturers re-validate the
AEDM that was used to certify the product within 30 days of receiving
the test report from the Department. DOE also proposed to require that
manufacturers incorporate DOE's test data into the re-validation of the
AEDM. If after inclusion of DOE's test data and re-validation, the
AEDM-certified ratings change for any models, then the manufacturer
would be required to re-rate and re-certify those models. The
manufacturer would not be required to perform additional testing in
this re-validation process unless the manufacturer finds it necessary
in order to meet the requirements enumerated in the proposed section
429.70. 77 FR 32028, 32056.
A few stakeholders provided comments on the aforementioned
proposals. Zero Zone commented that the failure of a single test unit
to meet its certified rating should not automatically necessitate re-
validation, but suggested that the manufacturer should decide on the
appropriate course of action. (Zero Zone, No. 64 at p. 3) UTC/Carrier
commented that DOE should not require re-validation based on a single
unit's test result because the failure could be a result of a defective
unit. (UTC/Carrier, No. 56 at p. 2) Lennox opposed DOE's proposal to
require manufacturers to incorporate DOE test data into their AEDM if a
model is determined not to meet its certified rating because they
believe that DOE data may be erroneous and only the best available data
should be used to validate an AEDM. (Lennox, No. 46 at p. 5) JCI stated
that without additional information as to why a particular product
failed a test, it is not reasonable to assume that all models rated
with the AEDM must be re-rated. (JCI, No. 66 at pp. 9-10).
In consideration of the above mentioned comments, DOE proposed to
allay concerns via the proposal in section III.B.6, which provides
manufacturers an opportunity to review the data from DOE's testing and
present claims regarding testing validity. Based on these comments, DOE
also proposes an exception to re-validation of the AEDM in cases where
the determination of an invalid rating for that basic model is the
first for models certified with an AEDM. In such cases, the
manufacturer must conduct additional testing and re-rate and re-certify
the individual combinations within the basic model that were improperly
rated using the AEDM.
DOE also proposes that if DOE has determined that a manufacturer
made invalid ratings on individual combinations within two or more
basic models rated using the manufacturer's AEDM within a 24 month
period, the manufacturer must test the least efficient and most
efficient combination within each basic model in addition to the
combination specified in 429.16(a)(1)(ii). The twenty-four month period
begins with a DOE determination that a rating is invalid through the
process outlined above. If DOE has determined that a manufacturer made
invalid ratings on more than four basic models rated using the
manufacturer's AEDM within a 24-month period, the manufacturer may no
longer use an AEDM.
Finally, DOE proposes additional requirements for manufacturers to
regain the privilege of using an AEDM, including identifying the
cause(s) for failure, taking corrective action, performing six new
tests per basic model, and obtaining DOE authorization.
DOE created this proposal under the expectation that each
manufacturer will use only a single AEDM for all central air
conditioner and central air conditioning heat pumps. DOE requests
comment on whether manufacturers would typically apply more than one
AEDM and if they would, the differences between such AEDMs.
8. Action Following a Determination of Noncompliance
In the AEDM NOPR, DOE explained that if a model failed to meet the
applicable Federal energy conservation standard during assessment
testing, DOE may pursue enforcement testing pursuant to 10 CFR 429.110.
DOE also stated that if an individual model was determined to be
noncompliant, then all other individual models within that basic model
would be considered noncompliant. This is consistent with
[[Page 69298]]
DOE's approach for all covered products. All other basic models rated
with the AEDM would be unaffected pending additional investigation.
Furthermore, DOE proposed that if a noncompliant model was used for
validation of an AEDM, the AEDM must be re-validated within 30 days of
notification, pursuant to requirements enumerated in 10 CFR 429.70.
Notably, DOE did not propose that manufacturers must re-test basic
models used to validate an AEDM when there is no determination of
noncompliance. 77 FR 32056.
In response, JCI agreed that all AEDM-rated models should not be
disqualified if one model is found out of compliance. (JCI, No. 66 at
p. 9)
DOE reiterates that for central air conditioners and central air
conditioning heat pumps, if an individual combination was determined to
be noncompliant, then all other individual combinations within that
basic model would be considered noncompliant. DOE is not proposing in
this SNOPR that other basic models rated with the AEDM be considered
non-compliant. However, DOE notes that an AEDM must be validated using
test data for individual combinations that meet the current Federal
energy conservation standards. Therefore, if a noncompliant model was
used for validation of an AEDM, manufacturers would be expected to re-
validate the AEDM in order to continue using it. The requirements for
additional testing based on invalid ratings, as discussed in the
previous section, may also apply.
C. Waiver Procedures
10 CFR 430.27(l) requires DOE to publish in the Federal Register a
notice of proposed rulemaking to amend its regulations so as to
eliminate any need for the continuation of waivers and as soon
thereafter as practicable, DOE will publish a final rule in the Federal
Register. As of the issuance date of this notice, a total of four
waivers (and one interim waiver) for central air conditioner and heat
pump products are active. They are detailed in the Table III.4, with
the section reference to this notice included for discussion regarding
DOE's proposed amended regulations and intention for subsequent waiver
termination.
Table III.4--Active Waivers and Active Interim Waivers
------------------------------------------------------------------------
Air Conditioners and Heat Pumps, Consumer
-------------------------------------------------------------------------
Scope Decision & order Termination
------------------------------------------------------------------------
ECR International, Inc., Multi- (Petition & Interim III.C.2
zone Unitary Small Air Waiver, 78 FR
Conditioners and Heat Pumps. 47681, 8/6/2013).
Daikin AC (Americas), Inc., Heat 76 FR 11438, 3/2/ III.C.1
Pump & Water Heater Combination. 2011.
Daikin AC (Americas), Inc., Heat 75 FR 34731, 6/18/ III.C.1
Pump & Water Heater Combination. 2010.
Hallowell International, Triple- 75 FR 6013, 2/5/2010 III.C.4
Capacity Northern Heat Pumps.
Cascade Group, LLC, Multi-blower 73 FR 50787, 8/28/ III.C.3
Air-Conditioning and Heating 2008.
Equipment.
------------------------------------------------------------------------
DOE notes that four waivers previously associated with both
commercial equipment and consumer products, as listed in Table III.3,
were terminated for consumer products as of the October 22, 2007 Final
Rule (72 FR 59906, 59911) and for commercial equipment as of the May
16, 2012 Final Rule (77 FR 28928, 28936). In this SNOPR, DOE reaffirms
that these waivers have been terminated for consumer products and that
the products in question can be tested using the current and proposed
test procedure for central air conditioners and heat pumps.
Table III.5--Terminated Waivers
------------------------------------------------------------------------
Scope Decision & order
------------------------------------------------------------------------
Daikin U.S. Corporation, Multi-split Heat 73 FR 39680, 7/10/2008.
Pumps and Heat Recovery Systems.
Mitsubishi Electric and Electronics USA, 72 FR 17528, 4/9/2007.
Inc., Variable Refrigerant Flow Zoning
Air Conditioners and Heat Pumps.
Fujitsu General Limited, Multi-split 72 FR 71383, 12/17/2007.
Products.
Samsung Air Conditioning, Multi-split 72 FR 71387, 12/17/2007.
Products.
------------------------------------------------------------------------
1. Termination of Waivers Pertaining to Air-to-Water Heat Pump Products
With Integrated Domestic Water Heating
DOE has granted two waivers to Daikin Altherma for the air-to-water
heat pump with integrated domestic water heating; one on June 18, 2010
and a second on March 2, 2011. 75 FR 34731 and 76 FR 11438. As
described in Daikin's petitions, the Daikin Altherma system consists of
an air-to-water heat pump that provides hydronic space heating and
cooling as well as domestic hot water functions. It operates either as
a split system with the compressor unit outdoors and the hydronic
components in an indoor unit, or as a single-package configuration in
which all system components are combined in a single outdoor unit. In
both the single-package and the split-system configurations, the system
can include a domestic hot water supply tank that is located indoors.
These waivers were granted on the grounds that the existing DOE test
procedure contained in Appendix M to Subpart B of 10 CFR part 430
addresses only air-to-air heat pumps and does not include any
provisions to account for the operational characteristics of an air-to-
water heat pump, or any central air-conditioning heat pump with an
integrated domestic hot water component.
According to the definition set forth in EPCA and 10 CFR 430.2, a
central air conditioner is a product, other than a packaged terminal
air conditioner, which is powered by single phase electric current, air
cooled, rated below 65,000 Btu per hour, not contained within the same
cabinet as a furnace, the rated capacity of which is above 225,000 Btu
per hour, and is a heat pump or a cooling unit only. (42 U.S.C.
6291(21)) The heat pump definition in EPCA and 10 CFR 430.2 requires
that a heat pump utilize a refrigerant-to-
[[Page 69299]]
outdoor air heat exchanger, effectively excluding heat pump products
classified as air-to-water. (42 U.S.C. 6291(24)) In addition, because
the definition of a central air conditioner, which also applies to heat
pumps, requires products to be ``air cooled,'' products that rely
exclusively on refrigerant-to-water heat exchange on the indoor side
are effectively excluded from the definition of, and the existing
efficiency standards for, central air conditioners and heat pumps.
Based upon the description in the waiver petitions for the Daikin
Altherma air-to-water heat pumps with integrated domestic water heater,
DOE has determined that these products rely exclusively on refrigerant-
to-water heat exchange on the indoor side, and thus would not be
subject to the central air conditioner or heat pump standards and would
not be required to be tested and rated for the purpose of compliance
with DOE standards for central air conditioners or heat pumps. Thus, if
this interpretation is adopted, these waivers would terminate on the
effective date of a notice finalizing the proposals in this notice.
2. Termination of Waivers Pertaining to Multi-Circuit Products
DOE granted ECR International (ECR) an interim waiver on August 6,
2013, for its line of Enviromaster International (EMI) products. 78 FR
47681. ECR describes in its petitions that its multi-zone air
conditioners and heat pumps each comprise a single outdoor unit
combined with two or more indoor units, which each comprise a
refrigeration circuit, a single air handler, a single control circuit,
and an expansion valve, intended for independent zone-conditioning. The
outdoor unit contains one fixed-speed compressor for each refrigeration
circuit; all zones utilize the same condenser fan and defrost
procedures but refrigerant is not mixed among the zones. 78 FR at
47686. These products are similar to multiple-split (or multi-split)
air conditioners or heat pumps, which are defined and covered by
current test procedure (Appendix M to Subpart B of 10 CFR part 430).
However, they are distinct from, and therefore not classified as,
multi-split products due to differences in refrigerant circuitry. The
separate refrigeration circuits of the ECR product line are not
amenable to the test procedures for multi-split systems, specifically
the procedures calling for operation at different levels of compressor
speed or staging, because the individual compressors are not
necessarily variable-speed. Hence, alternative procedures have been
developed, as described in the interim waiver. DOE proposes to address
products such as the ECR product line in the DOE test procedure. DOE
also proposes to define such a product as a ``multi-circuit air
conditioner or heat pump'' and provide testing requirements for such
for such products at 10 CFR 429.16(a)(1)(ii)(A).
For the duration of the interim waiver period, either until 180
days after the publication of the interim waiver (the interim waiver
period) or until DOE issued its determination on the petition for
waiver, whichever occurred earlier, DOE granted ECR permission to use
the proposed alternative test procedure to test and rate its multi-
circuit products. 78 FR 47681, 47682 (Aug. 6, 2013). The requirements
in the alternative test procedure comprise methods to establish air
volume rate, procedures for testing, and adjustments to equations used
to calculate SEER and HSPF. Following publication of the Notice of
Grant of Interim Waiver, DOE received no comments regarding this
alternative test procedure. After the interim waiver period, DOE did
not issue a final decision and order on ECR's petition for waiver,
therefore, the interim waiver will terminate upon the publication of a
test procedure final rule for central air conditioners and heat pumps,
and the alternative test procedure included therein shall cease from
being applicable to testing and rating ECR's multi-circuit products and
multi-circuit products in general, absent amendments regarding
provisions for testing such products. Therefore, DOE proposes in this
notice testing requirements for manufacturers who wish to certify
multi-circuit products.
According to Appendix M to Subpart B of 10 CFR part 430, Section
2.4.1b, systems with multiple indoor coils are tested in a manner where
each indoor unit is outfitted with an outlet plenum connecting to a
common duct so that each indoor coil ultimately connects to an airflow
measuring apparatus.\10\ In testing a multi-circuit system in this
manner, the data collection, performance measurement, and reporting is
done only on the system level. ECR took issue with this, citing
inadequate data accountability, and thus argued in its petition for
waiver to individually test each indoor unit. Id. Current test
procedures for systems with multiple indoor coils, however, produce
ratings that are repeatable and accurate even though monitoring of all
indoor units are not required by regulation, or common industry
practice. DOE also notes that the common duct testing approach has been
adopted by industry standards and is an accepted method for testing
systems having multiple indoor units. ECR's petition did not identify
specific differences between the indoor units of its new product line
and the indoor units of multi-splits that would make the common-duct
approach unsuitable for its products. Further, the interim waiver
approach of using multiple airflow measuring devices, one for each
indoor unit, represents unnecessary test burden. Therefore, DOE
proposes to adopt for multi-circuit products the same common duct
testing approach used for testing multi-split products.
---------------------------------------------------------------------------
\10\ When the indoor units are installed in separate indoor
chambers for the test, the test procedure allows common ducting to a
separate airflow measuring apparatus for each indoor chamber.
---------------------------------------------------------------------------
The alternative test procedure in the interim waiver calls for
separate measurement of performance for each indoor unit for each
required test condition, and requires that all indoor units be
operating during each of these separate measurements. The overall
system performance for the given test condition is calculated by
summing the capacities and power inputs measured for all of the indoor
units and adding to the power input sum the average of the power
measurements made for outdoor unit for the set of tests. Id. In
contrast, DOE's current proposal involves use of the common duct to
measure the full system capacity, thus allowing use of a single test
for each operating condition. DOE requests comment on whether this
method will yield accurate results that are representative of the true
performance of these systems.
3. Termination of Waiver and Clarification of the Test Procedure
Pertaining to Multi-Blower Products
On August 28, 2008, DOE published a decision and order granting
Cascade Group, LLC a waiver from the Central Air Conditioner and Heat
Pump Test Procedure for its line of multi-blower indoor units that may
be combined with one single-speed heat pump outdoor unit, one two-
capacity heat pump outdoor unit, or two separate single-speed heat pump
outdoor units. 73 FR 50787, 50787-97. DOE proposed revisions to the
test procedure in the June 2010 NOPR to accommodate the certification
testing of such products. 75 FR 31237. NEEA responded in the subsequent
public comment period, recommending DOE defer action on test procedure
changes until such a product is actually being tested, certified and
sold. (NEEA, No. 7 at pp. 4-5). Mitsubishi recommended DOE either use
AHRI Standard 1230-2010 to rate such a product or does not amend the
[[Page 69300]]
test procedure to allow coverage of such a product. (Mitsubishi, No. 12
at p. 2).
DOE notes that AHRI Standard 1230-2010, which provides testing
procedures for products with variable speed or multi-capacity
compressors, may not be suitable for testing the subject products,
which are equipped with single-speed compressors; however, the test
procedure, as proposed in the June 2010 NOPR enables testing of such
products. DOE therefore retains its proposal in the June 2010 NOPR to
adopt that test procedure, except for the following revisions.
The proposal in the June 2010 NOPR amended Appendix M to Subpart B
of 10 CFR part 430 with language in sections 3.1.4.1.1e and 3.1.4.2e
that suggested that test setup information may be obtained directly
from manufacturers. DOE is revising that proposal to eliminate the need
for communication between third-party test laboratories and
manufacturers, such that the test setup is conducted based on
information found in the installation manuals included with the unit by
the manufacturer. DOE is proposing that much of that information be
provided to DOE as part of certification reporting. These proposed
modifications regarding test setup can be found in section 3.1.4.1.1d
and 3.1.4.2e of the proposed Appendix M in this notice. DOE requests
comment on its proposals for multi-blower products, including whether
individual adjustments of each blower are appropriate and whether
external static pressures measured for individual tests may be
different.
Because the proposed test procedure amendments would allow testing
of Cascade Group, LLC's line of multi-blower products, DOE proposes to
terminate the waiver currently in effect for those multi-blower
products effective 180 days after publication of the test procedure
final rule.
4. Termination of Waiver Pertaining to Triple-Capacity, Northern Heat
Pump Products
On February 5, 2010, DOE granted Hallowell International a waiver
from the DOE Central Air Conditioner and Heat Pump Test Procedure for
its line of boosted compression heat pumps. 75 FR 6014, 6014-18. DOE
proposed revisions to its test procedures in the June 2010 NOPR to
accommodate the certification testing of such products. 75 FR 31223,
31238 (June 2, 2010). NEEA expressed support for DOE's proposal in the
subsequent public comment period but urged DOE to ensure that the
northern climate test procedure can be used by variable speed systems
that can meet the appropriate test conditions, and that the procedures
can accurately assess the performance of these systems relative to more
conventional ones. (NEEA, No. 7 at p. 5). NEEA also urged DOE to
require publishing of Region V ratings for heat pumps. Mitsubishi
supported DOE's proposed changes to cover triple-capacity, northern
heat pumps but requested that DOE reevaluate the testing of inverter-
driven compressor systems to permit better demonstration of the
system's capabilities at heating at low ambient conditions.
(Mitsubishi, No. 12 at p. 3).
DOE believes that the test procedure as proposed in the June 2010
NOPR, along with the proposed revisions to the test procedure for
heating tests conducted on units equipped with variable-speed
compressors, as discussed in section III.H.5, would produce performance
that represents an average period of use of such products. Because the
proposed test procedure amendments would allow testing of Hallowell
International's line of triple-capacity, northern heat pump products,
DOE proposes to terminate the waiver currently in effect for those
products effective 180 days after publication of the test procedure
final rule.
D. Measurement of Off Mode Power Consumption
In the June 2010 NOPR, DOE proposed a first draft of testing
procedures and calculations for off mode power consumption. 75 FR
31223, 31238 (June 2, 2010). In the following April 2011 SNOPR, DOE
proposed a second draft, revising said testing procedures and
calculations based on stakeholder-identified issues and changes to the
test procedure proposals in the 2010 June NOPR and on DOE-conducted
laboratory testing. 76 FR 18105, 18111 (April 1, 2011). In the October
2011 SNOPR, DOE proposed a third draft, further revising the testing
procedures and calculations for off mode power consumption based
primarily on stakeholder comments regarding burden of test as received
during the April 2011 SNOPR comment period. 76 FR 65616, 65618-22 (Oct.
24, 2011). From the original and extended comment period of the October
2011 SNOPR DOE received stakeholder comments, which are the basis of
DOE's proposed fourth draft in this notice, further revising testing
procedures and calculations for off mode power consumption. None of the
proposals listed in this section impact the energy conservation
standard.
1. Test Temperatures
In the October 2011 SNOPR, DOE proposed to base the off mode power
consumption rating (PW,OFF) on an average of wattages P1 and P2, which
would be recorded at the different outdoor ambient temperatures of 82
[deg]F and 57 [deg]F, respectively. DOE intended that, for systems with
crankcase heater controls, the measurement at the higher ambient
temperature would measure the off mode contribution that was more
representative of the shoulder seasons. The lower measurement was
intended to represent off mode power use for an air conditioner during
the heating season. 76 FR at 65621.
In response to the October 2011 SNOPR, a joint comment from Pacific
Gas and Electric and Southern California Edison, hereafter referred to
as the California State Investor Owned Utilities (CA IOUs), and a joint
comment from the American Council for an Energy-Efficient Economy
(ACEEE) and Appliance Standards Awareness Program (ASAP) expressed
concern that the 57 [deg]F test point could create a loophole wherein a
crankcase heater could be designed to turn on just below 57 [deg]F and
result in an underestimation of the system's energy consumption. The
off mode power consumption would be underestimated because the energy
consumption of the crankcase heater would not be included in either P1
or P2. (CA IOUs, No. 33 at p. 2; ACEEE and ASAP, No. 34 at p. 2) A
joint comment from the Northwest Energy Efficiency Alliance (NEEA) and
the Northwest Power and Conservation Council (NPCC), hereafter referred
to as the Joint Efficiency Advocates, also disputed DOE's proposal to
test units at two fixed temperatures and disagreed with DOE's
contention that the proposed P2 test temperature (57 [deg]F) is
sufficiently low that the crankcase heater would be energized. (Joint
Efficiency Advocates, No. 35 at p. 3)
Both the CA IOUs and the Joint Efficiency Advocates proposed that
DOE require manufacturers to specify the temperature at which the
crankcase heater turns on and off, and then to run one off mode test 3-
5 [deg]F below the point at which the crankcase heater turns on (``on''
set point temperature) and the other off mode test 3-5 [deg]F above the
temperature at which the crankcase heater turns off (``off'' set point
temperature). (CA IOUs, No. 33 at p. 2; Joint Efficiency Advocates, No.
35 at p. 3) However, the Joint Efficiency Advocates only proposed this
rating method for constant wattage crankcase heaters. (Joint Efficiency
Advocates, No. 35 at p. 3) The Joint Efficiency Advocates stated that
two measurements are insufficient for systems that have a heater with
wattage that varies according to temperature and
[[Page 69301]]
suggested that the crankcase heater power for systems with variable
wattage be tested at three temperatures. Specifically, the Joint
Efficiency Advocates recommended testing at 3-5 [deg]F below the ``on''
set point temperature, at 47 [deg]F, and at 17 [deg]F. (Joint
Efficiency Advocates, No. 35 at p. 4) The Joint Efficiency Advocates
additionally recommended that systems with temperature-controlled
crankcase heaters should be tested for off mode power use when cold
(i.e., before the system is run). (Joint Efficiency Advocates, No. 35
at p. 4)
In the December 2011 extension notice for comments on the October
2011 SNOPR, DOE requested comment on the CA IOUs' suggestion that the
test procedure should measure P1 at a temperature that is 3-5 [deg]F
above the manufacturer's reported ``off'' set point and measure P2 at a
temperature that is 3-5 [deg]F lower than the ``on'' set point. 76 FR
79135 (Dec. 21, 2011). The Joint Efficiency Advocates commented in
support of the CA IOU proposal. (Joint Efficiency Advocates, No. 43 at
p. 2) However, they also reiterated that crankcase heater power for
systems with variable wattage should be tested at three temperatures,
namely, 3-5 [deg]F below the ``on'' set point temperature, 47 [deg]F,
and 17 [deg]F. (Joint Efficiency Advocates, No. 43 at p. 2)
AHRI commented that DOE should modify the test procedure by having
up to three rating temperatures, depending on the manufacturer control
protocol. The first test would be conducted at 72 [deg]F immediately
after the B, C, or D test to verify whether the crankcase heater is on.
The second test would be conducted at 5 [deg]F below the temperature at
which the manufacturer specifies the crankcase heater turns on. The
third test would be conducted at 5 [deg]F below the temperature at
which the crankcase heater turns off and would only apply to air
conditioners with crankcase heater controls that turn off the crankcase
heater during winter. AHRI commented that it could accept the CA IOUs
proposal to test at 3-5 [deg]F below the heater turn-on temperature and
at 3-5 [deg]F above the heater turn-off temperature if DOE did not
accept AHRI's proposal. (AHRI, No. 41 at p. 2) Goodman commented in
support of AHRI's recommendation. (Goodman, No. 42 at p. 1)
Many of the commenters' recommended changes are reflected in this
proposed rule. DOE proposes to require manufacturers to include in
certification reports the temperatures at which the crankcase heater is
designed to turn on and turn off for the heating season, if applicable.
These temperatures are used in the proposed tests described in the
following paragraphs.
DOE proposes to replace the off mode test at 82 [deg]F with a test
at 722 [deg]F and replace the off mode test at 57 [deg]F
with a test at a temperature which is 52 [deg]F below a
manufacturer-specified turn-on temperature. This approach maintains the
intent of the off mode power consumption rating (PW,OFF) as a
representation of the off mode power consumption for the shoulder and
heating seasons, addresses AHRI's proposed modification of the test
procedure, and addresses ACEEE and ASAP's concerns regarding the
potential for a loophole at the 57 [deg]F test point.
DOE does not propose to adopt an additional test point at a
temperature of 17 [deg]F, as recommended by the stakeholders;
(Efficiency Advocates, No. 35 at p. 4; AHRI, No. 41 at p. 2) at a
temperature 5 [deg]F below the temperature at which the crankcase
heater turns off, as recommended by AHRI; (AHRI, No. 41 at p. 2) or at
a temperature 3-5 [deg]F above the heater turn-off temperature, as
recommended by the CA IOUs and the Joint Efficiency Advocates. (CA
IOUs, No. 33 at p. 2; Joint Efficiency Advocates, No. 35 at p. 3)
Manufacturer literature provides data on variable wattage crankcase
heaters, otherwise known as self-regulating crankcase heaters, which
show that power input for such heaters is a linear function of outdoor
ambient temperature (i.e., the input power can be represented with
insignificant error as a constant times the outdoor ambient temperature
plus another constant). As such, DOE maintains that two test points are
adequate for characterizing the off mode power consumption for self-
regulating crankcase heaters by establishing a linear fit from the two
test outputs. DOE also believes that one of the two test points is
adequate for characterizing the off mode power consumption for constant
wattage crankcase. DOE does not believe that the additional accuracy
gained from additional test points merits the additional test burden.
The modifications in this proposal should help to minimize the test
burden while maintaining the accuracy of off mode power ratings. DOE
requests comments on these proposals.
2. Calculation and Weighting of P1 and P2
Stakeholders submitted comments discussing the most appropriate way
to weight P1 and P2 in order to measure the total off mode power draw.
In the October 2011 SNOPR, DOE proposed to require calculation of the
total off mode power consumption based upon an arithmetic mean of the
power readings P1 and P2. 76 FR 65616, 65621 (Oct. 24, 2011).
The Joint Efficiency Advocates opposed the DOE's proposal in the
October 2011 SNOPR. (Joint Efficiency Advocates, No. 35 at p. 4) The CA
IOUs proposed to weight P1 by 25% and P2 by 75%, because this weighting
would be more representative of actual heater operation than equally
weighting P1 and P2. (Joint Utilities, No. 33 at p. 2) Conversely,
Goodman and AHRI opposed the CA IOUs' proposal because there was
inadequate data available to support weighting P1 by 25% and P2 by 75%.
Further, Goodman and AHRI stated that the CA IOUs' proposal would not
fairly differentiate between products with different crankcase heater
turn-on and turn-off temperatures. A unit with a lower turn-on and a
higher turn-off temperature would consume less overall energy, but a
manufacturer would have no incentive to use the lowest possible
temperatures because the rating would not change. (Goodman, No. 42 at
p. 2; AHRI, No. 41 at p. 3)
AHRI, Goodman, and the Joint Efficiency Advocates suggested that
average power should be calculated by weighting the off mode hours
using a bin method, in a manner consistent with the calculations of
seasonal active-mode. (AHRI, No. 41 at p.3; Goodman, No. 42 at p. 1;
Joint Efficiency Advocates, No. 35 at p. 5; Joint Efficiency Advocates,
No. 43 at p. 3) AHRI provided a detailed methodology for calculating
the off mode power rating in an excel spreadsheet submitted with its
written comments. (AHRI, No. 41 at p. 2) AHRI introduced bin
calculations to calculate seasonal P1 and P2 values, including
recommending a different set of fractional bin-hours for the shoulder
season. Goodman supported AHRI's proposal. (Goodman, No. 42 at p. 1)
However, AHRI and Goodman commented that if DOE did not accept AHRI's
proposed calculation, DOE should implement a 50% weighting of P1 and P2
as proposed in the October 2011 SNOPR. (AHRI, No. 41 at p. 3; Goodman,
No. 42 at p. 2)
After reviewing the Off-Mode Power excel spreadsheet from AHRI and
the comments received from stakeholders, DOE retains its proposal from
the October 2011 SNOPR, which gives equal weighting to P1 and P2 for
the calculation of the off mode power rating (PW,OFF). 76 FR 65616,
65620 (Oct. 24, 2011). Comments from the stakeholders did not provide
any data that support selection of specific weights for P1 and P2.
Therefore DOE cannot confirm that AHRI's suggested temperature bin-hour
calculation method is representative of
[[Page 69302]]
the off mode power for the shoulder and heating seasons.
3. Products With Large, Multiple or Modulated Compressors
In the October 2011 SNOPR, DOE proposed to adjust the measured off
mode power draw for systems with multiple compressors and apply a
scaling factor to systems larger than 3 tons. 76 FR at 65621-22. The CA
IOUs and the Joint Efficiency Advocates disagreed with DOE's approach.
(Joint Efficiency Advocates, No. 35 at p. 5; CA IOUs, No. 33 at p. 2;
CA IOUs, No. 40 at p. 1) The CA IOUs commented that adjusting the off
mode power draw for systems with multiple compressors and applying a
scaling factor to extra-large systems would not represent actual off
mode power consumption and recommended that DOE not reduce the
calculated off mode power based on the number of compressors. (CA IOUs,
No. 33 at p. 2)
AHRI and Goodman disagreed with CA IOUs' suggestion to eliminate
the adjustment based on the number of compressors as it may potentially
discourage the development and use of higher efficiency products.
(AHRI, No. 36 at p. 2; AHRI, No. 41 at p. 3; Goodman, No. 42 at p. 2)
Moreover, AHRI requested that a similar credit be given to products
using modulating compressors due to the typical application where a
higher charge is a requirement of the high efficiency systems. (AHRI,
No. 36 at p. 2) AHRI also disagreed with the idea of eliminating the
scaling factor proposed for rating larger compressors. (AHRI, No. 41 at
p. 3) Lastly, AHRI recommended that the measurement of the off mode
power consumption and of the low-voltage power from the controls for
the shoulder season be divided by the number of compressors or number
of discrete controls, as is currently done for the measurements in the
heating season. (AHRI, No. 36 at p. 2)
DOE is aware that some systems may require higher wattage heaters
to protect system reliability. Specifically, larger-capacity units may
have larger-capacity compressors, which (at a high level) have larger
shells with more surface area that can cool them off, thus requiring
more heater wattage. They may also have more lubricant, thus it takes
more heater wattage to heat up the lubricant to acceptable level (for
example after a power outage) before restart. To avoid situations that
force manufacturers to potentially compromise the reliability of their
systems by downsizing crankcase heater wattages to meet off mode power
requirements, DOE proposes to retain the recommended scaling factor for
large capacity systems.
Additionally, DOE does not want to penalize manufacturers of
multiple compressor systems, which are highly efficient but also need
to employ larger crankcase heaters for safe and reliable operation
given the additional shell surface area and lubricant. Therefore, DOE
agrees with AHRI's recommendation and proposes that the off mode power
consumption for the shoulder season and heating season, as well as the
low-voltage power from the controls, be divided by the number of
compressors to determine off mode power consumption on a per-compressor
basis.
The direct final rule also did not consider the possible
applicability of the new off mode standards to high-efficiency air
conditioners and heat pumps that achieve high SEER and HSPF ratings
using both large heat exchangers and compressor modulation. The
correlation of the use of modulating compressors with high refrigerant
charge, which is indicative of larger heat exchangers, was mentioned in
the AHRI comment. (AHRI, No. 41 at p. 3) DOE does not want to penalize
manufacturers for selling high efficiency units. Therefore, DOE agrees
with AHRI's recommendation to apply a multiplier to the calculation of
the per-compressor off mode power for the shoulder season and heating
season for modulated compressors, but proposes a multiplier of 1.5, as
modulating technology is not a multiple-compressor technology (with a
multiplier of 2+). DOE requests comment on the multiplier of 1.5 for
calculating the shoulder season and heating season per-compressor off
mode power for modulated compressors.
4. Procedure for Measuring Low-Voltage Component Power
In the October 2011 SNOPR, DOE proposed to measure the power from
low-voltage components, Px, after each of the two tests conducted at T1
and T2. 76 FR 65628-30. Although this would ensure that the low-voltage
power consumption at each temperature test point would be removed from
the respective off mode power consumption, AHRI expressed concern about
excessive manufacturer test burden. AHRI recommended that Px
not be re-measured, as it does not change with temperature and not re-
measuring it avoids automatic and unwanted operation of the crankcase
heater. (AHRI, No. 36 at p. 3)
DOE agrees with AHRI that the low voltage power consumption does
not change with temperature, although slight and insignificant
fluctuations in the low-voltage power may occur due to the relationship
of resistivity and conductivity to temperature. Moreover, DOE does not
believe that these fluctuations outweigh the test burden added from
reconfiguring the system for measuring the low-voltage power a second
time. As such, the test procedure has been revised so that the
measurement of Px is not repeated. DOE proposes to require that the
measurement of Px occur after the measurement of the heating season
total off mode power, P2x, which reduces test burden by requiring a
single disconnection of the low-voltage wires.
Additionally, DOE is aware that many control types exist for
crankcase heaters, and certain control methodologies cycle the
crankcase heater on and off during the 5-minute interval during which
Px is being measured. Since Px measures the power of functioning
components, only non-zero values of measured power should be used in
the calculations. DOE has therefore included in the proposed test
procedure a requirement to record only non-zero data for the
determination of Px.
5. Revision of Off-Mode Power Consumption Equations
As a result of the proposed revisions to the test procedure
discussed in section III.D.3 and section III.D.4, the equations from
the October 2011 SNOPR for determining P1 for crankcase heaters without
controls and for determining P2 for crankcase heaters with controls are
simplified in this proposal. The revised equations are:
[[Page 69303]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.000
respectively. 76 FR 65616, 65629-30 (Oct. 24, 2011). P1D is
the off mode power with the crankcase heater disconnected, which is
equal to the low-voltage power, Px. P1x is the shoulder-season total
off mode power, P2x is the heating-season total off mode power, P1 is
the per-compressor shoulder-season total off mode power, and P2 is the
per-compressor heating-season total off mode power.
The proposed revisions to section III.D.3 (per-compressor
representation of P1) and section III.D.4 (temperature-independence of
Px) of this notice allow for the simplification of the equations that
would be used to calculate power for crankcase heaters with or without
controls. The two proposed revisions are based on the following three
premises: (1) The representations of P1 and P2 would both be calculated
on a per-compressor basis (as discussed in section III.D.3); (2) The
value of Px would not vary with temperature and would thus be the same
at T1 as it is at T2 (as discussed in section III.D.4); (3) The
following would apply under the proposed method: P2 = P2x - Pxi P1 =
P1x - Px. (As discussed in the October 2011 SNOPR at 76 FR
65629). Applying the three premises to the equations for P1 and P2 from
the October 2011 SNOPR results in the following simplification:
[GRAPHIC] [TIFF OMITTED] TP09NO15.001
6. Off-Mode Power Consumption for Split Systems
AHRI commented that language in the October 2011 SNOPR may have
caused stakeholders to infer that every blower coil indoor unit
combination and every coil-only indoor unit combination must be tested
to determine off mode power consumption. (AHRI, No. 36 at p. 2) AHRI
recommended that DOE only require testing of the outdoor condensing
unit for the highest sale-volume combination of each basic model to
determine the off mode power consumption and allow use of an
alternative rating method (ARM) to reduce test burden. (AHRI, No. 36 at
p. 2)
In this SNOPR, DOE proposes generally that each basic model would
be required to have all applicable represented values (SEER, EER, HSPF,
or PW,OFF) of a specified individual combination determined
through testing. The other individual combinations within each basic
model may be tested or rated using AEDMs. As such, only one individual
combination within each basic model would be required to be tested to
determine off mode power consumption.
Additionally, upon reviewing the test procedures of furnace
products, DOE found that the indoor off mode power in coil-only split-
systems (that would be installed in the field with a furnace) was
accounted for in the furnace test methodology. The indoor power for
coil-only systems consists of the controls for the electronic expansion
valve drawing power from control boards either indoor in the furnace
assembly or outdoor in the condensing unit. To avoid double-counting
indoor off mode power between two products, DOE proposes to exclude
measurement of the low-voltage power if the controls for the indoor
components receive power from a control board dedicated to a furnace
assembly. For blower coil indoor units in which the air mover is a
furnace, the same proposal applies. For blower coil indoor units in
which the designated air mover is not a furnace, since the off mode
power of the indoor components is not accounted for in any other
product's test methodology, DOE proposes to adopt language to include
the low-voltage power from the indoor unit when measuring off mode
power consumption for blower coil systems.
7. DOE requests comment on its proposal to exclude low-voltage
power from the indoor unit when measuring off mode power consumption
for coil-only split-system air conditioners and for blower coil split
system air conditioners for which the air mover is a furnace. DOE also
requests comment on its proposal to include the low-voltage power from
the indoor unit when measuring off mode power consumption for blower
coil split-system air conditioners with an indoor blower housed with
the coil and for heat pumps.
Time Delay Credit
To provide an additional incentive for manufacturers to reduce
energy consumption, AHRI and Goodman suggested adding a credit for
crankcase heaters that incorporate a time delay before turning on
during the shoulder season. (AHRI, No. 41 at p. 2; Goodman, No. 42 at
p. 1) The off mode period in the calculation methodology designates
extended periods during which the unit
[[Page 69304]]
is idle. DOE proposes to adopt an energy consumption credit that would
be proportional to the duration of the delay, as implemented in the
calculation of the off mode energy consumption for the shoulder season,
E1, in the proposed off mode test procedure. DOE is also proposing, for
products in which a time delay relay is installed but the duration of
the delay is not specified in the manufacturer's installation
instructions shipped with the product or in the certification report, a
default period of non-operation of 15 minutes out of every hour,
resulting in a 25% savings in shoulder-season off mode energy
consumption. To reduce potential instances of the misuse of this
incentive, DOE also proposes requiring manufacturers to report the
duration of the crankcase heater time delay for the shoulder season and
heating season that was used during certification testing. DOE is also
considering adding a verification method to 429.134. DOE requests
comment on the proposed method for accounting for the use of a time
delay, the default period of non-operation, and the possibility of a
verification test for length of time delay.
8. Test Metric for Off-Mode Power Consumption
The June 2010 NOPR proposed a test procedure that would measure the
average off mode power consumption, PW,OFF, of a central air
conditioner or heat pump. 75 FR 31238-39. Additionally, the amended
energy conservation standards for central air conditioners and heat
pumps in the June 2011 DFR included standards for off mode power
consumption that were defined in terms of PW,OFF. 76 FR 37408, 37411.
The Joint Efficiency Advocates and the CA IOUs commented that the test
procedure should calculate energy use and not average power draw.
(Joint Efficiency Advocates, No. 43 at p. 3; CA IOUs, No. 33 at p. 1)
The CA IOUs stated that DOE should measure energy use because control
systems on the crankcase heater can save power by reducing run time,
which is not captured by a power-draw metric. (CA IOUs, No. 33 at p. 1)
The Joint Efficiency Advocates also requested that any standards
promulgated should be based on energy use. (Joint Efficiency Advocates,
No. 43 at p. 2) To maintain consistency with the off mode standards,
the test procedure must measure off mode power consumption rather than
energy use. However, DOE recognizes that adopting a bin-based approach
to calculate PW,OFF does not provide a final off mode value that is
indicative of actual power consumption. DOE is aware of alternative
methods to determine a power rating. However, in consideration of
testing burden, DOE proposes to implement a method of calculation that
would closely approximate the actual off mode power consumption via a
simple average of the shoulder and heating season measured values.
Although this metric will not directly translate into instantaneous off
mode power consumption, annual energy costs, or national energy
consumption, it does provide a standardized method of calculation that
is representative of average off mode power consumption. The average
off mode power calculation can be used for ranking models based on
their performance when idle, as well as for comparing a model's
performance to the DOE standards.
DOE is aware that measurement of energy use for a specified test
period would enable calculation of annual energy consumption and
operating costs and, on a larger scale, national energy savings and
national energy consumption solely due to equipment idling. Therefore,
DOE has proposed optional equations that a manufacturer could use to
determine the actual off mode energy consumption, based on the hours of
off mode operation and off mode power for the shoulder and heating
seasons, to provide additional information to consumers. Energy
consumption would be specific to a single location and its unique set
of cooling, heating, and shoulder season hours. DOE requests comment on
such equations.
9. Impacts on Product Reliability
AHRI and Bristol Compressors submitted comments expressing concern
that regulating crankcase heater energy consumption could have a
negative impact on product reliability (AHRI, No. 41 at pp. 1-2;
Bristol, No. 39 at p. 1) Bristol Compressors remarked that simply
turning the crankcase heater off at specific outdoor ambient
temperatures would expose many compressors to conditions that would
reduce the effective life of the product or, at worst, cause immediate
failure. Bristol requested that DOE allow additional time for research
on technological options that could save energy in a manner similar to
controls based on outdoor ambient temperature, but that do not impact
the reliability of the product. (Bristol, No. 39 at p. 1) AHRI asked
DOE to conduct further research to determine if regulating crankcase
heater energy consumption has a negative impact on product reliability
and to consider additional amendments to the test procedure, if deemed
necessary, to limit impacts on product reliability. (AHRI, No. 41 at p.
2)
DOE expects that this proposed off mode test method will allow
manufacturers to meet the June 2011 off mode standards without causing
a shift in the reliability of the overall market of central air
conditioners and heat pumps. DOE requests comments on the issue of
compressor reliability as it relates to crankcase heater operation in
light of the test method proposed in this rule.
10. Representative Measurement of Energy Use
In the April 2011 SNOPR DOE proposed modifications to the
laboratory tests and algorithms for determining the off mode power of
central air conditioners and heat pumps. 76 FR 18105, 18107-09 (April
1, 2011). DOE received comments indicating that the April 2011 SNOPR
was overly burdensome, and the October 2011 SNOPR proposed a revised
method that was intended to reduce this burden. 76 FR 65616 (Oct. 24,
2011).
Following the October 2011 SNOPR, the Joint Efficiency Advocates
stated that, while minimizing test burden is important, DOE is also
obligated by statute to prescribe a test procedure that measures the
energy use of a covered product during a representative average use
cycle or period of use. (42 U.S.C. 629(b)(3)) The Joint Efficiency
Advocates stated that the Department's proposal was far from
accomplishing that statutory requirement. (Joint Efficiency Advocates,
No. 35 at p. 2) The CA IOUs noted that the test procedure revisions
presented in the October 2011 SNOPR would not encourage innovative
designs of heating systems in off mode, and that the results produced
by the test procedure would be misleading to consumers, because the
reported values would not be indicative of actual power draw if DOE
were to require measurements based on fixed outdoor temperatures and
use a simple average of P1 and P2. (CA IOUs, No. 33 at p. 1)
However, in the December 2011 extension notice, DOE proposed to
consider the suggestion by the CA IOUs to use the actual outdoor
temperatures at which the crankcase heater turns on or off to measure
P1 and P2, as discussed in section III.D.2. The CA IOUs subsequently
submitted comments that reaffirmed this proposal, and recommended that
DOE consider its proposals to use a weighted average of P1 and P2 and
to not adjust power draw for systems with multiple compressors or
large-capacity systems. (CA IOUs, No. 40 at p.1) The Joint Efficiency
Advocates conveyed strong support for
[[Page 69305]]
the CA IOUs' proposal and remarked that the test procedure would not be
indicative of actual energy use if DOE did not adopt the CA IOUs'
proposal. (Joint Efficiency Advocates, No. 43 at p. 1; Joint Efficiency
Advocates, No. 43 at p. 3)
As previously discussed, DOE must develop test procedures to
measure energy use that balance test burden with measurement accuracy.
The off mode test procedures published in the original NOPR and the
first SNOPR were judged by stakeholders to be too complex and
burdensome. As a result, DOE proposed a test method in the second SNOPR
that was simplified and designed to result in comparatively less test
burden. The simplified test procedure, however, may have impacted the
ability to provide a measurement that is representative of an average
use cycle or period of use. In this third SNOPR, DOE has made
additional revisions and believes that this new proposed off mode test
procedure limits test burden to a reasonable extent and will provide a
means for measuring off mode power use in a representative manner.
E. Test Repeatability Improvement and Test Burden Reduction
42 U.S.C. 6293(b)(3) states that any test procedure prescribed or
amended shall be reasonably designed to produce test results which
measure energy efficiency and energy use of a covered product during a
representative average period of use and shall not be unduly burdensome
to conduct. This section discusses proposals to improve test procedure
clarity and to reduce test burden. None of the proposals listed in this
section would alter the average measured energy consumption of a
representative set of models.
1. Indoor Fan Speed Settings
Indoor unit fan speed is typically adjustable during test set-up to
assure that the provided air volume rate is appropriate for the field-
installed ductwork system serving the building in which the unit is
actually installed. The DOE test procedure accounts for these variable
settings by establishing specific requirements for external static
pressure and air volume rate during the test. For an indoor coil tested
with an indoor fan installed, DOE's test procedure requires that (a)
external static pressure be not less than a minimum value that depends
on cooling capacity \11\ and product class, ranging from 1.10 to 1.20
inches of water column (in. wc.) for small-duct, high-velocity systems
and from 0.10 to 0.20 in. wc. for all other systems except non-ducted
units (see 10 CFR part 430, subpart B, Appendix M, Table 2); and (b)
the air volume rate divided by the total cooling capacity not exceed a
maximum value of 37.5 cubic feet per minute of standard air (scfm) per
1000 Btu/h of cooling capacity \12\ (see 10 CFR part 430, subpart B,
Appendix M, Section 3.1.4.1.1).
---------------------------------------------------------------------------
\11\ Or heating capacity for heating-only heat pumps.
\12\ Such a requirement does not exist for heating-only heat
pumps.
---------------------------------------------------------------------------
Requirement (a) is more easily met using higher fan speeds, while
requirement (b) is more easily met by lower fan speeds. DOE realizes
that more than one speed setting may meet both the minimum static
pressure and the maximum air volume rate requirements. Section
3.1.4.1.1(a)(6) of the current DOE test procedure for air conditioners
and heat pumps allows adjustment of the fan speed to a higher setting
if the first selected setting does not meet the minimum static pressure
requirement at 95 percent of the cooling full-load air volume rate.\13\
This step suggests that common test practice would be to initially
select lower fan speeds to meet the requirements before attempting
higher speeds. However, the test procedure does not, for cases in which
two different settings could both meet the air volume rate and static
pressure requirements, explicitly specify that the lower of the two
settings should be used for the test. The fan power consumption would
generally be less at lower speeds, but compressor power consumption may
be reduced at conditions of higher air volume rate--hence it is not
known prior to testing whether a higher or lower air volume rate will
maximize the SEER or HSPF for a given individual model. However, DOE is
aware that efficiency ratings are generally better when products are
tested at the lowest airflow-control settings intended for cooling (or
heating) operation that will satisfy both the minimum static pressure
and maximum air volume rate requirements. DOE therefore proposes that
blower coil products tested with an indoor fan installed be tested
using the lowest speed setting that satisfies the minimum static
pressure and the maximum air volume rate requirements, if applicable,
if more than one of these settings satisfies both requirements. This is
addressed in section 2.3.1.a of Appendix M.
---------------------------------------------------------------------------
\13\ For heating-only heat pumps, Section 3.1.4.4.3(a)(6) allows
adjustment of the fan speed to a higher setting if the first
selected setting does not meet the requirements minimum static
pressure requirement at 95 percent of the heating full-load air
volume rate.
---------------------------------------------------------------------------
For a coil-only system, i.e., a system that is tested without an
indoor fan installed, the pressure drop across the indoor unit must not
exceed 0.3 inches of water for the A test (or A2 test for
two-capacity or variable-capacity systems), and the maximum air volume
rate per capacity must not exceed 37.5 cubic feet per minute of
standard air (scfm) per 1000 Btu/h. (10 CFR part 430, subpart B,
Appendix M, Section 3.1.4.1.1) For such systems, higher air volume
rates enhance the heat transfer rate of the indoor coil, and therefore
may maximize the measured system capacity and efficiency. In addition,
the energy use and heat input attributed to the fan energy for such
products is a fixed default value in the test procedure, and is set at
365 W per 1,000 scfm (10 CFR part 430, subpart B, Appendix M, Section
3.3(d)). Thus, the impact from fan power on the efficiency measurement
if air volume rate is increased may be more modest than for a unit
tested with the indoor fan installed. However, a maximum external
static pressure of 0.3 in. wc. is specified for the indoor coil
assembly in order to represent the field-installed conditions. To
minimize potential testing variability due to the use of different air
volume rates, DOE proposes to require for coil-only systems for which
the maximum air flow (37.5 scfm/1000 Btuh) or maximum pressure drop
(0.3 in wc) are exceeded when using the specified air flow rate, the
highest air flow rate that satisfies both the maximum static pressure
and the maximum air volume rate requirements should be used. This is
specified in section 3.1.4.1.1.c of Appendix M.
Improper fan speed implemented during testing may have a marked
impact on product performance, and inconsistent implementation of speed
adjustments may be detrimental to test repeatability. DOE therefore
proposes to require that manufacturers include in their certification
report the speed setting and/or alternative instructions for setting
fan speed to the speed upon which the rating is based.
For consistency with the furnace fan test procedure, DOE proposes
to add to Appendix M (and also Appendix M1) the definition for
``airflow-control setting'' that has been adopted in Appendix AA to
refer to control settings used to obtain fan motor operation for
specific functions.
DOE requests comment on its proposals regarding requirements on fan
speed settings during test setup.
[[Page 69306]]
2. Requirements for the Refrigerant Lines and Mass Flow Meter
Section 2.2(a) of 10 CFR part 430, subpart B, Appendix M provides
instructions for insulating the ``low-pressure'' line(s) of a split-
system. In the cooling mode, the vapor refrigerant line connecting the
indoor and outdoor units is operating at low refrigerant pressure.
However, in the heating mode, the vapor refrigerant line connecting the
indoor and outdoor units operates at high pressure, providing high
pressure vapor to the indoor unit. To improve clarity and ensure that
the language of the test procedure refers specifically to the actual
functions of the refrigerant lines, DOE proposes to refer to the lines
as ``vapor refrigerant line'' and ``liquid refrigerant line''.
Section 2.2(a) of 10 CFR part 430, subpart B, Appendix M and AHRI
210/240-2008 Section 6.1.3.5 both require insulation on the vapor
refrigerant line and do not state what insulation, if any, is required
on the liquid refrigerant line. Differences in product design and in
the parts manufacturers decide to ship with the unit may lead to
varying interpretations regarding the need to insulate the liquid
refrigerant line during the test and may therefore introduce test
variability. Furthermore, there may be unnecessary burden on test
laboratories if they choose to add insulation when manufacturers do not
to ship liquid refrigerant line insulation with the unit. While DOE
wishes to clarify requirements for insulation of refrigerant lines,
there are two factors that make such a determination difficult: (1)
There may be reasons both for insulating and for not insulating the
liquid refrigerant tubing--if not insulated, additional subcooling of
the refrigerant liquid as it passes through the line prior to its
expansion in the indoor unit may increase cooling capacity and thus
increase the measured SEER. However, the increased subcooling of the
liquid would increase the load on the outdoor coil during the heating
mode of a heat pump, which may slightly reduce evaporating temperature
and thus both reduce heat pump capacity and increase compressor power
input. On the other hand, insulating the liquid line would result in
higher measurements of HSPF for a heat pump when compared with
measurements with the liquid line not insulated, but would result in
lower measurements of the SEER; (2) DOE has observed that installation
manuals for air conditioners and heat pumps generally indicate that
liquid lines should be insulated in special circumstances (e.g.,
running the line through a warm space or extra-long refrigerant line
runs), but do not provide guidance on the use of insulation in the
absence of such conditions.
Because DOE seeks to minimize test variability associated with the
use of insulation, this notice includes a proposal for determining the
insulation requirement for the test based on the materials and
information included by the manufacturer with the test unit. Under this
proposal, test laboratories would install the insulation shipped with
the unit. If the unit is not shipped with insulation, the test
laboratory would install the insulation specified in the installation
manuals included with the unit by the manufacturer. Should the
installation instructions not provide sufficient guidance on the means
of insulating, liquid line insulation would be used only if the product
is a heating-only heat pump. These proposed requirements are intended
to reduce test burden and improve test repeatability for cooling and
heating products, as well as heating-only products. DOE requests
comment on its proposal to require that test laboratories install the
insulation included with the unit or, if insulation was not furnished
with the unit, follow the insulation specifications in the
manufacturer's installation instructions. DOE also requests comment on
its proposal to require liquid line insulation of heating-only heat
pumps.
In cases where the refrigerant enthalpy method is used as a
secondary measurement of indoor space conditioning capacity,
uninsulated surfaces of the refrigerant lines and the mass flow meter
may also contribute to thermal losses. DOE does not believe that
preventing the incremental thermal losses associated with the mass flow
meter components and its support structure would make a measurable
impact on efficiency measurements. However, DOE does recognize the
possibility that thermal loss might reduce the efficiency measurement,
particularly during heating mode tests if the mass flow meter is placed
on the test chamber floor, which might be cooler than the air within
the room. To enhance test repeatability among various laboratories that
may use different mass flow meters with varying materials for support
structures, DOE proposes to require use of a thermal barrier to prevent
such thermal transfers between the flow meter and the test chamber
floor if the meter is not mounted on a pedestal or other support
elevating it at least two feet from the floor. DOE proposes to add
these requirements to Appendix M, section 2.10.3. DOE requests comment
on this means to prevent meter-to-floor thermal transfer.
3. Outdoor Room Temperature Variation
Depending on the operating characteristics of the test laboratory's
outdoor room conditioning equipment, temperature or humidity levels in
the room may vary during testing. For this reason, a portion of the air
approaching the outdoor unit's coil is sampled using an air sampling
device (see Appendix M, section 2.5). The air sampling device,
described in ASHRAE Standard 41.1-2013, consists of multiple manifolded
tubes with a number of inlet holes, and is often called an air sampling
tree. If, during testing, the air entering the outdoor unit of a
product is monitored only on one of its faces and there is significant
spatial variation of the room's air conditions, the measured conditions
for the monitored face may not be indicative of the average conditions
for the inlet air across all faces.
To ensure that the measurements account for variation in the
conditions in the outdoor room of the test chamber, DOE proposes to
require demonstration of air temperature uniformity over all of the
air-inlet surfaces of the outdoor unit using thermocouples, if sampling
tree air collection is performed only on one face of the outdoor unit.
Specifically, DOE would require that the thermocouples be evenly
distributed over the inlet air surfaces such that there is one
thermocouple measurement representing each square foot of air-inlet
area. The maximum temperature spread to demonstrate uniformity, i.e.,
the maximum allowable difference in temperature between the
measurements at the warmest location and at the coolest location, would
be 1.5 [deg]F (DOE proposes to add these requirements to Appendix M,
section 2.11.b). This is the same maximum spread allowable for
measurement of indoor unit capacity using thermocouple grids, as
described in 10 CFR part 430, subpart B, Appendix M, Section 3.1.8, in
which the maximum spread among the measured temperatures on the
thermocouple grid in the outlet plenum of the indoor coil must not
exceed 1.5[emsp14][deg]F dry bulb. If this specified measurement of
temperature uniformity cannot be demonstrated, DOE would require
sampling tree collection of air from all air-inlet surfaces of the
outdoor unit. DOE seeks comment for the proposed 1.5 [deg]F maximum
spread for demonstration of outdoor air temperature uniformity, the
proposed one square foot per thermocouple basis for thermocouple
distribution, and the proposed requirement that an air
[[Page 69307]]
sampling device be used on all outdoor unit air-inlet surfaces if
temperature uniformity is not demonstrated. DOE proposes to add these
requirements to Appendix M, section 2.11.b.
4. Method of Measuring Inlet Air Temperature on the Outdoor Side
To ensure test repeatability, DOE seeks to ensure that temperature
measurements taken during the test are as accurate as possible. DOE is
aware that measurement of outdoor inlet temperatures is commonly based
on measurements of the air collected by sampling devices that use high-
accuracy dry bulb temperature and humidity measurement devices, and
that the accuracy of these devices may be better than that of
thermocouples. DOE proposes to require that the dry bulb temperature
and humidity measurements, that are used to verify that the required
outdoor air conditions have been maintained, be measured for the air
collected by the air sampling devices (e.g., rather than being measured
by temperature sensors located in the air stream approaching the air
inlets). DOE requests comment on this proposal.
5. Requirements for the Air Sampling Device
In evaluating various test setups and laboratory conditions, DOE
has observed that certain setup conditions of the air sampling
equipment could lead to measurement error or variability between
laboratories. Specifically, the temperature of air collected by indoor
and outdoor room air sampling devices could potentially change as it
passes through the air collection system, leading to inaccurate
temperature measurement if the air collection devices or the conduits
conducting the air to the measurement location are in contact with the
chamber floor or with ambient air at temperatures different from the
indoor or outdoor room. To prevent this potential cause of error or
uncertainty, DOE proposes to require that no part of the room air
sampling device or the means of air conveyance to the dry bulb
temperature sensor be within two inches of the test chamber floor. DOE
also proposes to require those surfaces of the air sampling device and
the means of air conveyance that are not in contact with the indoor and
outdoor room air be insulated.
A potential contributor to error or uncertainty in the measurement
of humidity is the taking of dry bulb and wet bulb measurements in
different locations, if there is significant cool down of air between
the two locations. While ASHRAE Standard 41.1-2013 provides an example
of an air sampling device with a dry bulb and wet bulb thermometer
placed close together, the figure is merely illustrative. To minimize
measurement error or uncertainty, DOE proposes to require that humidity
measurements and dry bulb temperature measurements used to determine
the moisture content of air be made at the same location in the air
sampling device.
As discussed in section III.E.14, DOE has also proposed several
amendments to air sampling procedures that are included in a draft
revision of AHRI 210/240-2008. DOE requests comments on all of these
related proposals, including its proposal to require that the air
sampling device and its components be prevented from touching the test
chamber floor, to require insulation of those surfaces of the air
sampling device and components that are not in contact with the chamber
room air, and that dry bulb temperature and humidity measurements used
to determine the moisture content of air be made at the same location
in the air sampling device.
6. Variation in Maximum Compressor Speed With Outdoor Temperature
When testing an air conditioner or heat pump with a variable-speed
compressor, the compressor must be tested at three different speeds:
Maximum, intermediate, and minimum. Some air conditioners and heat
pumps with a variable-speed compressor operate such that their maximum
allowed compressor speed varies with the outdoor temperature. However,
the test procedure does not explicitly state whether the maximum
compressor speed refers to a fixed value or a temperature-dependent
value. As such, DOE proposes that the maximum compressor speed be fixed
during testing through modification of the control algorithm used for
the particular product such that the speed does not change with the
outdoor temperature. DOE requests comment on this proposal.
7. Refrigerant Charging Requirements
Near-azeotropic and zeotropic refrigerant blends are composed of
multiple refrigerants with a range of boiling points. Gaseous charging
of refrigerant blends is inappropriate because it can result in higher
concentrations of the higher-vapor pressure constituents being charged
into the unit, which can alter refrigerant performance characteristics
and thus, unit performance. DOE recognizes that technicians certified
to handle refrigerants via the Environment Protection Agency's (EPA)
Section 608 Technician Certification Program, as mandated by 40 CFR
82.161, are required to be knowledgeable of charging methods for
refrigerant blends. However, to ensure consistent practices within the
context of the DOE test procedure, DOE proposes to require that near-
azeotropic and zeotropic refrigerant blends be charged in the liquid
state rather than the vapor state. This is found in section 2.2.5.8 of
Appendix M. DOE requests comments on this proposal.
Current language in Appendix M to Subpart B of 10 CFR part 430 does
not prohibit testers from changing the amount of refrigerant charge in
a system during the course of air conditioner and heat pump performance
tests. Changing the amount of refrigerant may result in a higher SEER
and/or a higher HSPF that does not reflect the actual performance of a
unit in the field. In the June 2010 NOPR, DOE proposed to adopt into
the test procedure select parts of the 2008 AHRI General Operations
Manual that contains language disallowing changing the refrigerant
charge after system setup. (75 FR 31234-5) AHRI and NEEA supported this
proposal. (AHRI, No. 6 at p. 3; NEEA, No. 7 at p. 4) To ensure that
performance tests reflect operation in the field, and to improve
consistency in results between test facilities, DOE intends to retain
the proposal made in the June 2010 NOPR. Specifically, DOE retains the
proposed requirement that once the system has been charged with
refrigerant consistent with the installation instructions shipped with
the unit (or with other provisions of the test procedure, if the
installation instructions are not provided or not clear), all tests
must be conducted with this charge.
DOE is aware that refrigerant charging instructions are different
for different products, but that in some cases, such instructions may
not be provided. More specifically, the appropriate charging method may
vary among products based upon their refrigerant metering devices. The
thermostatic expansion valve (TXV) type metering device is designed to
maintain a specific degree of superheat.\14\ Electronic expansion valve
(EXV) type metering devices function similarly to TXV type metering
devices, but use sensors, a control system, and an actuator to set the
valve position to allow more sophisticated control of the degree of
superheat. Fixed orifice is
[[Page 69308]]
another type of expansion device commonly used for air conditioners. In
contrast to a TXV or EXV, a fixed orifice does not actively respond to
system pressures or temperatures to maintain a fixed degree of
superheat. The refrigerant charge can affect the measured system
efficiency. Systems with different expansion devices react differently
to variation in the charge, and they also generally require different
procedures for ensuring that the system is properly charged. As the
charging operation may differ among these types of metering devices,
and misidentification may lead to inconsistent charging and
unrepeatable testing, DOE proposes to require manufacturers to report
the type of metering device used during certification testing.
---------------------------------------------------------------------------
\14\ The degree of superheat is the extent to which a fluid is
warmer than its bubble point temperature at the measured pressure,
i.e., the difference between a fluid's measured temperature and the
saturation temperature at its measured pressure.
---------------------------------------------------------------------------
If charging instructions are not provided in the manufacturer's
installation instructions shipped with the unit, DOE proposes
standardized charging procedures to ensure consistent testing in a
manner that reflects field practices. For a unit equipped with a fixed
orifice type metering device for which the manufacturer's installation
instructions shipped with the unit do not provide refrigerant charging
procedures, DOE proposes that the unit be charged at the A or
A2 test condition, requiring addition of charge until the
superheat temperature measured at the suction line upstream of the
compressor is 12 [deg]F with tolerance discussed in section III
E.14.\15\ For a unit equipped with a TXV or EXV type metering device
for which the manufacturer's installation instructions shipped with the
unit do not provide refrigerant charging procedures, DOE proposes that
the unit be charged at the A or A2 condition, requiring
addition of charge until the subcooling \16\ temperature measured at
the condenser outlet is 10 [deg]F with tolerance discussed in section
III E.14.\17\
---------------------------------------------------------------------------
\15\ The range of superheating temperatures was generalized from
industry-accepted practice and state-level authority regulations on
refrigerant charging for non-TXV systems.
\16\ The degree of subcooling or subcooling temperature is the
extent to which a fluid is cooler than its refrigerant bubble point
temperature at the measured pressure, i.e., the bubble point
temperature at a fluid's measured pressure minus its measured
temperature. Bubble point temperature is the temperate at a given
pressure at which vapor bubbles just begin to form in the
refrigerant liquid.
\17\ The range of subcooling temperatures was generalized from
manufacturer-published and technician-provided service instructions
and are typical of industry practice.
---------------------------------------------------------------------------
For heating-only heat pumps for which refrigerant charging
instructions are not provided in the manufacturer's installation
instructions shipped with the unit, the proposed standardized charging
procedure would be followed while performing refrigerant charging at
the H1 or H12 condition. DOE also proposes that charging be
done for the H1 or H12 test condition for cooling/heating
heat pumps which fail to operate properly in heating mode when charged
using the standardized charging procedure for the A or A2
test condition. In such cases, some of the tests conducted using the
initial charge may have to be repeated to ensure that all tests
(cooling and heating) are conducted using the same refrigerant charge.
DOE proposes to add these requirements to Appendix M in a new section
2.2.5.8.
DOE requests comments on the proposed standardized charging
procedures to be applied to units for which the installation
instructions shipped with the unit do not provide charging
instructions.
DOE understands that manufacturers may provide installation
instructions with different charging procedures for the indoor and
outdoor units. In such cases, DOE proposes to require charging based on
the installation instructions shipped with the outdoor unit for outdoor
unit manufacturer products and based on the installation instructions
shipped with the indoor unit for independent coil manufacturer
products, unless otherwise specified by either installation
instructions. DOE requests comments on this proposal.
Single-package central air conditioners and heat pumps may be
shipped with refrigerant already charged into the unit. Verifying the
proper amount of refrigerant charge is valuable for increasing test
repeatability. To this end, DOE believes that the benefits of
installing pressure gauges on a single-package unit to help verify
charge and to monitor refrigerant conditions generally outweigh the
potential drawbacks associated with connecting the gauges (e.g.,
refrigerant transfer from the product into the gauges and hoses or
refrigerant leakage); calculating the superheat or subcooling
quantities used to determine whether the unit is charged properly
requires knowledge of the refrigerant pressure, and the quantity of
charge transferred from the unit when connecting a pressure gauge set
is generally a very small percentage of the unit's charge. Further,
assessing the refrigerant charge may improve repeatability of the tests
and measured efficiency. DOE therefore proposes that refrigerant line
pressure gauges be installed during the setup of single-package and
split-system central air conditioner and heat pump products, unless
otherwise specified by the instructions. DOE also proposes that the
refrigerant charge be verified per the charging instructions and, if
charging instructions are not provided in the installation instructions
shipped with the unit, the refrigerant charge would be verified based
on the standardized charging procedure described above. DOE requests
comments on these proposals.
As discussed in section III.E.14, DOE has also proposed several
amendments to charging procedures that are included in a draft revision
of AHRI 210/240-2008. DOE requests comment on all aspects of its
proposals to amend the refrigerant charging procedures.
8. Alternative Arrangement for Thermal Loss Prevention for Cyclic Tests
10 CFR part 430, subpart B, Appendix M, Section 2.5(c) requires use
of damper boxes in the inlet and outlet ducts of ducted units to
prevent thermal losses during the OFF period of the compressor OFF/ON
cycle for the cooling or heating cyclic tests. However, DOE is aware
that installation of such dampers for single-package ducted units can
be burdensome because the unit must be located in the outdoor chamber
and there may be limited space in the chamber and in between the inlet
and outlet ducts to install the required transition ducts, insulation,
and dampers. To preserve the intent of the air damper boxes, reduce
testing burden, and accommodate variations in chamber size, DOE
proposes an alternative testing arrangement to prevent thermal losses
during the compressor OFF period that would eliminate the need to
install a damper in the inlet duct that conveys indoor chamber air to
the indoor coil.
The proposed alternative testing arrangement would allow the use of
a duct configuration that relies on changes in duct height, rather than
a damper, to eliminate natural convection thermal transfer out of the
indoor duct during OFF periods of the ``cold'' or heat generated by the
system during the ON periods. An example of such an arrangement would
be an upturned duct installed at the inlet of the indoor duct, such
that the indoor duct inlet opening, facing upwards, is sufficiently
high to prevent natural convection transfer out of the duct. DOE also
proposes to require installation of a dry bulb temperature sensor near
the inlet opening of the indoor duct at a centerline location not
higher than the lowest elevation of the duct edges at the inlet.
Measurement and recording of dry bulb temperature at this location
would be required at least every minute during the compressor OFF
period to confirm that no thermal loss occurs. DOE
[[Page 69309]]
proposes a maximum permissible variation in temperature measured at
this location during the OFF period of 1.0 [deg]F.
DOE seeks comment on its proposal in section 2.5(c) of Appendix M
to allow, for cyclic tests, alternative arrangements to replace the
currently-required damper in the inlet portion of the indoor air
ductwork for single-package ducted units. DOE also requests comment on
the proposed requirements for ensuring that there are no thermal losses
during the OFF portion of the test, including the location of the
proposed dry bulb temperature sensor, the requirements for recorded
temperatures, and the 1.0 [deg]F allowable variation in
temperature measured by this sensor.
9. Test Unit Voltage Supply
The current DOE test procedure references ARI Standard 210/240-2006
Section 6.1.3.2 for selecting the proper electrical voltage supply,
which generally requires that, for tests performed at standard rating
conditions (referred to as ``Standard Rating tests'' in Standard 210/
240), the tests be conducted at the product's nameplate rated voltage
and frequency. This section also requires that Standard Rating tests be
performed at 230 V for air-cooled equipment rated with 208-230 V dual
nameplate voltages, and that all other dual nameplate voltage equipment
be tested at both voltages or at the lower of the two voltages if only
a single Standard Rating is to be published. DOE recognizes that
nameplate voltages may differ for indoor and outdoor units. This may
result in a difference of voltage supplied to the indoor and outdoor
units in accordance with the current test requirement. DOE realizes
that, in most cases, this voltage difference that may occur during
testing is not representative of field operation where indoor and
outdoor units are typically supplied with the same voltage. As such,
DOE proposes to clarify that the outdoor voltage supply requirement
supersedes the indoor requirement if the provisions result in a
difference for the indoor and outdoor voltage supply. That is, both the
indoor and outdoor units shall be tested at the same voltage supplied
to the outdoor unit.
10. Coefficient of Cyclic Degradation
The cooling coefficient of degradation, Cc, is the ratio of the EER
measured for cycling (or intermittent) operation to the EER that would
be measured for steady operation. The heating coefficient of
degradation, Ch, is a similar factor that characterizes efficiency
reduction for cycling operation during heat pump operation. The test
procedures to determine these two coefficients are the same except for
the testing conditions and unit operation mode, and the changes
discussed in this section are applied to both metrics. Therefore, for
the sake of simplicity and clarity, only the cooling coefficient of
degradation is discussed here.
The current test procedure gives manufacturers the option to use a
default cyclic degradation coefficient (CD) value of 0.25
instead of running the optional cyclic test. In response to the June
2010 NOPR, which proposed some modifications related to the optional
tests but not the default value, NEEA commented that its laboratory
testing demonstrated that the default value 0.25 is not representative
of system performance, especially for TXV-equipped systems, and instead
supported using the actual tested values in determining ratings. (NEEA,
No. 7 at pp. 6-7) DOE reviewed results from its own testing of 19
split-system and single-package air conditioners and heat pumps from
1.5 to 5 tons and found that the tested CD values range from
0.02 to 0.18, with an average of 0.09. It also found no correlation
between CD and SEER, EER, or cooling capacity. DOE also
reviewed the AHRI 210/240-Draft (see section III.E.14), which updates
the cooling Cc value to 0.2. DOE believes this default value may be
more in-line with actual tested values, and DOE proposes to update the
default cooling Cc value in Appendix M to 0.2. At this time, DOE is not
proposing to update the default heating Ch value. In evaluating
appropriate default values, DOE also reviewed its testing requirements
to measure CD.
DOE is aware of various issues that occur when conducting the test
procedure to measure the degradation coefficient, such as the inability
to attain stable capacity measurements from cycle to cycle and
burdensome testing time to attain stability, and believes that these
are symptoms of cyclic instability. DOE believes that the variation in
cooling capacity during the test to determine Cc is exacerbated by the
short compressor on-time specified for each cycle and by the effect of
response time, sensitivity, and repeatability errors. DOE understands
the importance of having a minimally burdensome test procedure.
However, DOE recognizes that the current test method for measuring Cc,
although clear in description and intent, does not provide requirements
for cyclic stability of measured capacity over successive on-cycles
during the test. Therefore, DOE proposes the following procedure based
on cyclic testing data to clarify the test procedure, address cyclic
stability, and offer default procedures to allow for test burden
relief.
DOE has obtained cyclic test data that show that as cycles are
tested, either capacity reaches steady-state or capacity fluctuates
constantly and consistently. Therefore, DOE proposes that before
determining Cc, three ``warm up'' cycles for a unit with a single-speed
compressor or two-speed compressor or two ``warm up'' cycles for a unit
with a variable speed compressor must be conducted. Then, conduct a
minimum of three complete cycles after the warm-up period, taking a
running average of Cc after each additional cycle. If after three
cycles, the average of three cycles does not differ from the average of
two cycles by more than 0.02, the three-cycle average should be used.
If it differs by more than 0.02, up to two more valid cycles will be
conducted. If the average Cc of the last three cycles are within 0.02
of or lower than the previous three cycles, use the average Cc of all
valid cycles. After the fifth valid cycle, if the average Cc of the
last three cycles is more than 0.02 higher than the previous three
cycles, the default value will be used. The same changes are proposed
for the test method to determine the heating coefficient of
degradation.
Given these changes to address, DOE proposes that unlike the
current test procedure, manufacturers must conduct the specified
testing required to measure CD for each tested unit. The
default value may only be used if stability or the test tolerance is
not achieved or when testing outdoor units with no match.
DOE requests comment regarding the proposed revisions to the cyclic
test procedure for the determination of both the cooling and heating
coefficient of degradation. DOE also requests additional test data that
would support the proposed specifications, or changes to, the number of
warm-up cycles, the cycle time for variable speed units, the number of
cycles averaged to obtain the value, and the stability criteria.
11. Break-In Periods Prior to Testing
On June 1, 2012, AHRI submitted a supplement to the comments it
submitted on January 20, 2012, as part of the extended comment period
on the October 2011 SNOPR. In these supplementary comments, AHRI
requested that DOE implement an optional 75-hour break-in period for
testing central air conditioners and heat pumps. It stated that scroll
compressors, which are the type of compressors most
[[Page 69310]]
commonly used in central air conditioners and heat pumps, achieve their
design efficiency after 75 hours of operation, so the allowance for a
break-in period of this length would ensure that the product being
tested is operating as intended by the manufacturer and would provide a
result that is more representative of average use. AHRI also cited a
study of compressor break-in periods to justify this period of
time,\18\ and added that, while AHRI's certification program for
central air conditioners and heat pumps does not specify a minimum
break-in period, it does allow manufacturers to specify a break-in
period for their products. According to AHRI's comments, some
manufacturers request a break-in period in excess of 100 hours, while
others request 50 hours or less.
---------------------------------------------------------------------------
\18\ Khalifa, H.E. ``Break-in Behavior of Scroll Compressors''
(1996). International Compressor Engineering Conference. Paper 1145.
---------------------------------------------------------------------------
Furthermore, AHRI commented that implementation of an optional
break-in period for central air conditioners and heat pumps would be
consistent with a similar provision in the DOE test procedures for
commercial heating and air-conditioning equipment, which DOE adopted in
a final rule published May 16, 2012. 77 FR 28928. As stated in the
final rule, the purpose of including this option for testing commercial
HVAC equipment was to ensure that the equipment being tested would have
time to achieve its optimal performance prior to conducting the test.
DOE placed a maximum limit of 20 hours on the allowed period of break-
in, regardless of the break-in period recommended by the manufacturer,
explaining that such a limit was necessary to minimize the burden
imposed by this provision. In addition, DOE required that manufacturers
who use the optional break-in period report the duration of their
break-in as part of the test data underlying the certification that is
required to be maintained under 10 CFR 429.71. DOE stated that it would
use the same break-in period for any DOE-initiated testing as the
manufacturer used in its certified ratings or, in the case of ratings
based upon use of an alternate efficiency determination method (AEDM),
the maximum 20-hour break-in period. 77 FR 28928, 28944.
After consideration of the potential improvement in performance and
increased test burden that may result from implementation of an
optional 75-hour break-in period, DOE believes that the lengthy break-
in period is not appropriate or justified. In reviewing the paper that
AHRI cited in its comments, DOE noted that, while the data indicate
that products with scroll compressors do appear to converge upon a more
consistent result after compressor break-in periods exceeding 75 hours,
the most significant improvement in compressor performance and
reduction in variation among compressor models both appear to occur
during roughly the first 20 hours of run time.\19\ Moreover, scroll
compressors in use at the time of this paper's publication in 1996 may
have required longer break-in periods to address the surface quality of
the internal components resulting from the manufacturing processes of
that time, whereas compressors in use today have benefitted from
improvements in the manufacturing technology for scroll compressors
over the past 20 years. In addition, while the paper also supports
AHRI's comment that smaller compressors require more time to reach
their optimal performance than larger compressors, it does not show the
absolute size of the compressors that were studied and makes
comparisons based only on their relative sizes. Therefore, it is
difficult to precisely determine how this data would apply to a central
air conditioner or heat pump compressor versus a commercial air
conditioner or heat pump. Finally, since DOE determined in the May 16,
2012 commercial HVAC equipment final rule that a 20 hour maximum break-
in time would be sufficient for small commercial air-conditioning
products, which are of a capacity similar to central air-conditioning
products, DOE does not see justification for a break-in period longer
than 20 hours for products. 77 FR 28928.
---------------------------------------------------------------------------
\19\ Ibid. pp. 442-443.
---------------------------------------------------------------------------
In consideration of AHRI's comments on the merits of conducting a
break-in period prior to testing of central air conditioners and heat
pumps, DOE proposes in this SNOPR to allow manufacturers the option of
specifying a break-in period to be conducted prior to testing of these
products under the DOE test procedure. However, due to the excessive
test burden that could be imposed by allowing lengthy break-in times,
DOE proposes to limit the optional break-in period to 20 hours, which
is consistent with the test procedure final rule for commercial HVAC
equipment. DOE also proposes to adopt the same provisions as the
commercial HVAC rule regarding the requirement for manufacturers to
report the use of a break-in period and its duration as part of the
test data underlying their product certifications, the use of the same
break-in period specified in product certifications for testing
conducted by DOE, and use of the 20 hour break-in period for products
certified using an AEDM.
DOE requests comments on its proposal to allow an optional break-in
period of up to 20 hours prior to testing as part of the DOE test
procedure for central air conditioners and heat pumps.
12. Industry Standards That Are Incorporated by Reference
In the June 2010 NOPR, DOE proposed two ``housekeeping'' updates
throughout Appendix M regarding test procedure references. 75 FR 31243.
The first is an update of the incorporation by reference (IBR) from ARI
Standard 210/240-2006 to ANSI/AHRI 210/240-2008, which provides
additional test unit installation requirements and requirements on
apparatus used during testing. The second update involves changes to
references from 10 CFR 430.22 to 10 CFR 430.3, as the listing of those
materials incorporated by reference was relocated. In the public
comment period following the NOPR, AHRI expressed support for updating
the test procedure to reference current AHRI and ASHRAE standards.
(AHRI, No. 6 at p. 6). DOE is maintaining its position in the June 2010
NOPR for both proposals and therefore implemented the reference updates
in the reprint of Appendix M of this notice. However, DOE proposes in
this SNOPR to incorporate by reference the 210/240 standard having the
most recent amendments at the time of this notice, i.e., ANSI/AHRI 210/
240-2008 with Addendum 2.\20\ The changes incorporated by these
amendments relate to replacing the Integrated Part Load Value (IPLV)
efficiency metric with the Integrated Energy Efficiency Ratio (IEER)
metric, as well as adding the methodology for determining IEER for
water- and evaporatively-cooled products. These changes are relevant
only to commercial equipment and are not relevant to the DOE test
procedure for central air conditioners and heat pumps. Therefore
updating references to the latest version of ANSI/AHRI 210/240 will not
impact the ratings or energy conservation standards for central air
conditioners and heat pumps.
---------------------------------------------------------------------------
\20\ ANSI/AHRI 210/240-2008 with Addendum 2 is named as such but
includes changes per an Addendum 1 on the same standard.
---------------------------------------------------------------------------
In addition, in this SNOPR, DOE proposes to update the IBR from
ASHRAE Standard 37-2005, Methods of Testing for Rating Unitary Air-
Conditioning and Heat Pump Equipment to ASHRAE Standard 37-2009,
Methods of Testing for Rating Electrically Driven Unitary Air-
Conditioning and Heat Pump
[[Page 69311]]
Equipment; ASHRAE 41.9-2000, Calorimeter Test Standard Methods for Mass
Flow Measurements of Volatile Refrigerants to ASHRAE 41.9-2011,
Standard Methods for Volatile-Refrigerant Mass Flow Measurements Using
Calorimeters; and ASHRAE/AMCA 51-1999/210-1999, Laboratory Methods of
Testing Fans for Aerodynamic Performance Rating to ASHRAE/AMCA 51-07/
210-07, Laboratory Methods of Testing Fans for Certified Aerodynamic
Performance Rating. None of these updates includes significant changes
to the sections referenced in the DOE test procedure and thus will not
impact the ratings or energy conservation standards for central air
conditioners and heat pumps.\21\
---------------------------------------------------------------------------
\21\ ASHRAE 37-2009 only updates to more recent versions of
other standards it references. ASHRAE/AMCA 51-07/210-07 made slight
changes to the figure referenced by DOE, which DOE has determined to
be insignificant.
---------------------------------------------------------------------------
Additionally, DOE proposes to update the IBR from ASHRAE 41.1-1986
(Reaffirmed 2006), Standard Method for Temperature Measurement to
ASHRAE 41.1-2013, Standard Method for Temperature Measurement, as well
as the IBR to ASHRAE 41.6-1994, Standard Method for Measurement of
Moist Air Properties to ASHRAE 41.6-2014, Standard Method for Humidity
Measurement. In the updated versions of these standards, specifications
for measuring wet-bulb temperature were moved from ASHRAE 41.1 to
ASHRAE 41.6. None of these updates includes significant changes to the
sections referenced in the DOE test procedure and thus will not impact
the ratings or energy conservation standards for central air
conditioners and heat pumps.
Also, DOE proposes to update the IBR from ASHRAE 23-2005, Methods
of Testing for Rating Positive Displacement Refrigerant Compressors and
Condensing Units to ASHRAE 23.1-2010 Methods of Testing for Rating the
Performance of Positive Displacement Refrigerant Compressors and
Condensing Units That Operate at Subcritical Temperatures of the
Refrigerant. ASHRAE 23 has been withdrawn and has been replaced by
ASHRAE 23.1 and ASHRAE 23.2. ASHRAE 23.2 deals with supercritical
pressure conditions, which are not relevant to the DOE test procedure,
so will not be referenced. None of these updates includes significant
changes to the sections referenced in the DOE test procedure and thus
will not impact the ratings or energy conservation standards for
central air conditioners and heat pumps.
DOE also proposes to revise its existing IBRs to AHRI 210/240-2008
with Addendums 1 and 2, ANSI/AHRI 1230-2010 with Addendum 2, ASHRAE
23.1-2010 (updated from ASHRAE 23-2005), ASHRAE 37-2009 (updated from
2005), ASHRAE 41.1-2013 (updated from 1986 version), ASHRAE 41.2-1987,
ASHRAE 41.6-2014 (updated from 1994 reaffirmed in 2001 version), ASHRAE
41.9-2011 (updated from 2000 version), and ASHRAE/AMCA 51-07/210-07
(updated from 1999 version) to incorporate only the sections currently
referenced or proposed to be referenced in the DOE test procedure. DOE
requests comment on its proposed sections for incorporation and
specifically on whether any additional sections may be necessary to
conduct a test of a unit.
DOE also proposes to revise the definition of ``continuously
recorded'' based on changes to ASHRAE 41.1. ASHRAE 41.1-86 specified
the maximum time intervals for sampling dry-bulb temperature. The
updated version, ASHRAE 41.1-2013 does not contain specifications for
sampling intervals. DOE proposes to require that dry-bulb temperature,
wet bulb temperature, dew point temperature, and relative humidity data
be ``continuously recorded,'' that is, sampled and recorded at 5 second
intervals or less. DOE is proposing this requirement as a means of
verifying that temperature condition requirements are met for the
duration of the test. DOE requests comment on its revised sampling
interval for dry-bulb temperature, wet bulb temperature, dew point
temperature, and relative humidity.
13. Withdrawing References to ASHRAE Standard 116-1995 (RA 2005)
In the June 2010 NOPR, DOE proposed referencing ASHRAE Standard
116-1995 (RA 2005) within the DOE test procedure to provide additional
informative guidance for the equations used to calculate SEER and HSPF
for variable-speed systems. 75 FR 31223, 31243 (June 2, 2010). In the
subsequent public comment period, AHRI expressed support for DOE's
proposal to reference ASHRAE 116. (AHRI, No. 6 at p. 6). However, in
section III.H.4 of this notice, DOE proposes to change the heating load
line, and as such the equations for HSPF in ASHRAE Standard 116 are no
longer applicable. In order to prevent confusion, DOE proposes in this
notice to withdraw the proposal made in the June 2010 NOPR to reference
ASHRAE 116 for both HSPF and SEER and is removing those instances of
references to said standard from the test procedure.
Appendix M only references ASHRAE 116 in one other location,
regarding the requirements for the air flow measuring apparatus. Upon
review, DOE has determined that referencing ASHRAE Standard 37 instead
provides sufficient information. As a result, in this NOPR, DOE also
proposes to revise its reference for the requirements of the air flow
measuring apparatus to ASHRAE Standard 37-2009 rather than ASHRAE 116,
and proposes to remove the incorporation by reference to ASHRAE 116
from the code of federal regulations related to central air
conditioners and heat pumps.
14. Additional Changes Based on AHRI 210/240-Draft
In August 2015, AHRI provided a draft version of AHRI 210/240 for
the docket that will supersede the 2008 version once it is published.
(AHRI Standard 210/240-Draft, No. 45, See EERE-2009-BT-TP-0004-0045)
The draft version includes a number of revisions from the 2008 version,
some of which already exist in DOE's test procedure, and some of which
do not.
Regarding test installation requirements, the AHRI 210/240-Draft
added new size requirements for the inlet duct to the indoor unit. If
used, the inlet duct size to the indoor unit is required to equal the
size of the inlet opening of the air-handling (blower-coil) unit or
furnace, with a minimum length of 6 inches. Regarding the testing
procedure, the AHRI 210/240-Draft added new external static pressure
requirements for units intended to be installed with the airflow to the
outdoor coil ducted. These new requirements provide for testing of
these products more consistently with the way that they are intended to
be used in the field. Also regarding the testing procedure, the AHRI
210/240-Draft specified a new requirement for the dew point temperature
of the indoor test room when the air surrounding the indoor unit is not
supplied from the same source as the air entering the indoor unit. DOE
proposes to adopt these three revisions in this SNOPR.
The AHRI 210/240-Draft includes several differences as compared to
the current DOE test procedure for setting air volume rates during
testing. Specifically:
(a) Air volume rates would be specified by the manufacturer;
(b) For systems tested with indoor fans installed in which the fans
have permanent-split-capacitor (PSC) or constant-torque motors, there
would be minimum external static pressure requirements for operating
modes other than full-load cooling; and
[[Page 69312]]
(c) A criterion is defined for acceptable air flow stability for
systems tested with constant-air-volume indoor fans (these are fans
with controls that vary fan speed to maintain a constant air volume
rate).
DOE proposes to adopt these changes because they will improve
repeatability and the consistency of testing among different
laboratories.
The AHRI 210/240-Draft also includes a more thorough procedure for
setting of refrigerant charge than exists in the DOE test procedure.
The new approach addresses potential issues associated with conflicting
guidelines that might be provided by manufacturer's installation
instructions and indicates how to address ranges of target values
provided in instructions. DOE is proposing these changes because they
improve test repeatability. The AHRI 210/240-Draft also specifies both
a target value tolerance and a maximum tolerance but does not specify
in what circumstances each of these apply. DOE proposes to adopt the
maximum tolerance only. However, DOE may consider adopting only the
target value tolerance or both the target value and maximum tolerance.
DOE requests comment on the appropriate use of the target value and
maximum tolerances, as well as data to support the appropriate
selection of tolerance. DOE notes that the tolerances adopted in the
DOE test procedure should be achievable by test lab personnel without
the presence or direct input of the manufacturer.
Finally, the AHRI 210/240-Draft includes specifications for air
sampling that provide more detail than provided in existing standards.
DOE proposes to incorporate these specifications by reference in order
to improve test procedure repeatability and consistency. The proposal
currently cites the AHRI 210/240-Draft, which is not possible for the
final rule associated with this rulemaking. However, DOE expects that
the AHRI standard will be finalized in time to allow the final rule to
amend the CFR to incorporate this material.
DOE notes that the final published version of what is currently the
AHRI 210/240-Draft may not be identical to the current draft. If AHRI
makes other than minor editorial changes to the sections DOE references
in this SNOPR after publication of this SNOPR, DOE proposes to adopt
the current draft content into its regulations and not incorporate by
reference the modified test procedure.
15. Damping Pressure Transducer Signals
ASHRAE 37-2009, which DOE proposes in this SNOPR to be incorporated
by reference into the DOE test procedure, includes requirements for
maximum allowable variation of specific measurements for a valid test.
Specifically, Table 2 of the standard indicates that the test operating
tolerance (total observed range) of the nozzle pressure drop may be no
more than 2 percent of the average value of reading. Section 5.3.1 of
the standard indicates that the nozzle pressure drop (or the nozzle
throat velocity pressure) may be measured with manometers or electronic
pressure transducers. These measurements are made to determine air
flow. Section 8.7.2 of the standard requires that measurements shall be
recorded at equal intervals that span five minutes or less when
evaluating cooling capacity.
DOE is aware that when nozzle pressure drop measurements are made
with pressure transducers and recorded using a computer-based data
acquisition system, high frequency pressure fluctuations can cause
observed pressure variations in excess of the 2 percent test operating
tolerance, even when air flows are steady and non-varying. DOE proposes
to add clarifying language in the test procedure that would allow for
damping of the measurement system to prevent such high-frequency
fluctuations from affecting recorded pressure measurements. The
proposal would allow for damping of the measurement system so that the
time constant for response to a step change in pressure (i.e. the time
required for the indicated measurement to change 63% of the way from
its initial value to its final value) is no more than five seconds.
This damping could be achieved in any portion of the measurement
system. Examples of damping approaches include adding flow resistance
to the pressure signal tubing between the pressure tap and the
transducer, using a transducer with internal averaging of its output,
or filtering the transducer output signal, digital averaging of the
measured pressure signals. DOE requests comment on this proposal,
including on whether the proposed maximum time constant is appropriate.
F. Clarification of Test Procedure Provisions
Ensuring repeatability of test results requires that all parties
that test a unit use the same set of instructions to set up the unit,
conduct the test, and calculate test results. A test laboratory may be
tempted to contact the product's manufacturer or other sources of
information not referenced or allowed by the test procedure if there is
a lack of clarity in the installation instructions shipped with the
unit or ambiguities within the test procedure itself. Currently,
certain sections of the DOE test procedure for central air conditioners
and heat pumps in Appendix M to Subpart B of 10 CFR part 430 permit
such consultation with the manufacturer. In the June 2010 NOPR, DOE
proposed to allow lab-manufacturer communication as long as test unit
installation and laboratory testing are conducted in complete
compliance with all requirements in the DOE test procedure and the unit
is installed according to the manufacturer's installation instructions.
75 FR 31223, 31235 (June 2, 2010). In the subsequent public comment
period, AHRI expressed support regarding DOE's proposal. (AHRI, No. 6
at p. 3). Mitsubishi also supported adding test procedure to clarify
that interaction with the manufacturer is allowed. (Mitsubishi, No. 12
at p. 2). NEEA did not object to DOE's proposal. (NEEA, No. 7 at p. 4).
Because the reliance upon such consultation could lead to variability
in test results among laboratories by manufacturers providing different
testing instructions, DOE seeks to limit such occurrences to the
maximum extent possible by ensuring that all required testing
conditions and product setup information is either specified in the
test procedure, certified to DOE, or stated in installation manuals
shipped with the unit by the manufacturer. DOE believes that the
proposed revisions in this rule provide such clarity and allow for
models to be tested and rated in an equitable manner across
manufacturers. Upon implementing such clarifications, laboratories will
no longer need to contact the manufacturer for advice on implementation
of the test procedure. If questions arise about a specific test
procedure provision, the test lab and/or the manufacturer should seek
guidance from DOE. DOE believes that this change will eliminate
inconsistent testing due to different test laboratories seeking and
receiving different information regarding unclear instructions. Thus,
DOE proposes the following changes to the test procedure to address
test procedure provisions that may be ambiguous or unclear in their
intent and also withdraws the proposal it made in the June 2010 NOPR
that placed no restrictions on interactions between manufacturers and
third-party test laboratories 75 FR at 31235.
[[Page 69313]]
1. Manufacturer Consultation
DOE proposes to clarify the test procedure provisions regarding the
specifications for refrigerant charging prior to testing, with input on
certain details from the AHRI 210/240-Draft, as discussed in section
III.E.14. Section 2.2.5 of the test procedure provides refrigerant
charging instructions but also states, ``For third-party testing, the
test laboratory may consult with the manufacturer about the refrigerant
charging procedure and make any needed corrections so long as they do
not contradict the published installation instructions.'' The more
thorough refrigerant charging requirements proposed in this notice
should preclude the need for any manufacturer consultation, since they
include steps to take in cases where manufacturer's installation
instructions fail to provide information regarding refrigerant charging
or provide conflicting requirements. Consultation with the manufacturer
should thus become unnecessary, and DOE proposes to remove the current
test procedure's allowance for contacting the manufacturer to receive
charging instructions. In instances where multiple sets of instructions
are specified or are included with the unit and the instructions are
unclear on which set to test with, DOE proposed in the June 2010 NOPR
to use the instructions ``most appropriate for a normal field
installation.'' 75 FR 31235, 31250. (June 2, 2010) NEEA supported this
proposal. (NEEA, No. 7 at p. 4). DOE proposes to maintain this position
in this rulemaking, proposing the use of field installation criteria if
instructions are provided for both field and lab testing applications.
In the June 2010 NOPR, DOE proposed requirements for the low-
voltage transformer used when testing coil-only air conditioners and
heat pumps, and required metering of such low-voltage component energy
consumption during all tests. 75 FR 31238. In the April 2011 SNOPR, in
response to the June 2010 NOPR public meeting comments, DOE proposed
revised requirements such that metering of low-voltage component energy
consumption is required during only the proposed off mode testing,
citing that such changes would require adjustments to the standard
levels currently being considered. 76 FR 18109. The proposal therein
consisted of language that suggested that test setup information may be
obtained directly from manufacturers. In the effort to remain objective
during testing, DOE is hereby revising certain language in the proposal
such that communication between third party test laboratories and
manufacturers are eliminated, and such information when needed for test
setup can be found in the installation manuals included with the unit
by the manufacturer.
Regarding the use of an inlet plenum, section 2.4.2 of the test
procedure states, ``When testing a ducted unit having an indoor fan
(and the indoor coil is in the indoor test room), the manufacturer has
the option to test with or without an inlet plenum installed. Space
limitations within the test room may dictate that the manufacturer
choose the latter option.'' To eliminate the need for the test
laboratory to confirm with the manufacturer whether the inlet plenum
was installed during the manufacturer's test, DOE proposes to require
manufacturers to report on their certification report whether the test
was conducted with or without an inlet plenum installed.
Further, it is unclear in certain sections of the test procedure
which ``test setup instructions'' are to be referenced for preparing
the unit for testing. Ambiguous references to ``test setup
instructions'' and/or ``manufacturer specifications'' may lead to the
use of instructions or specifications provided by the manufacturer that
are possibly out-of-date or otherwise not applicable to the products
being tested. DOE therefore proposes to amend references in the test
procedure to test setup instructions or manufacturer specifications by
specifying that these refer to the test setup instructions included
with the unit. DOE proposes to implement this change in the following
sections: 2.2.2, 3.1.4.2(c), 3.1.4.4.2(c), 3.1.4.5(d), and 3.5.1(b)(3).
2. Incorporation by Reference of ANSI/AHRI Standard 1230-2010
ANSI/AHRI Standard 1230-2010 ``Performance Rating of Variable
Refrigerant Flow (VFR) Multi-Split Air-Conditioning and Heat Pump
Equipment'' with Addendum 2 (AHRI Standard 1230-2010) prescribes test
requirements for both consumer and commercial variable refrigerant flow
multi-split systems. On May 16, 2012, DOE incorporated this standard by
reference into test procedures for testing commercial variable
refrigerant flow multi-split systems at 10 CFR 431.96. 77 FR 28928. DOE
recognizes that consumer variable refrigerant flow multi-split systems
have similarities to their commercial counterparts. Therefore, to
maintain consistency of testing consumer and commercial variable
refrigerant flow multi-split systems, DOE proposes to incorporate by
reference the sections of AHRI Standard 1230-2010 that are relevant to
consumer variable refrigerant flow multi-split systems (namely,
sections 3 (except 3.8, 3.9, 3.13, 3.14, 3.15, 3.16, 3.23, 3.24, 3.26,
3.27, 3.28, 3.29, 3.30, and 3.31), 5.1.3, 5.1.4, 6.1.5 (except Table
8), 6.1.6, and 6.2) into the existing test procedure for central air
conditioners and heat pumps at Appendix M to Subpart B of 10 CFR part
430. To ensure that there is no confusion with future definition
changes in industry test procedures, DOE is including the terms
``Multiple-split (or multi-split) system'', ``Small-duct, high-velocity
system'', ``Tested combination'', ``Variable refrigerant flow system''
and ``Variable-speed compressor system'' into its list of definitions
in Appendix M to Subpart B of 10 CFR part 430.
10 CFR 429.16 requires the use of a ``tested combination,'' as
defined in 10 CFR 430, subpart B, Appendix M, section 1.B, when rating
multi-split systems. In response to a May 27, 2008 letter from AHRI to
DOE, DOE proposed changes in the ``tested combination'' definition in
the June 2010 NOPR. 75 FR 31223, 31231 (June 2, 2010). In comments
responding to the NOPR, AHRI urged DOE to adopt AHRI Standard 1230-2010
for all requirements pertaining to multi-split systems. (AHRI, No. 6 at
pp. 1-2) Mitsubishi recommended likewise. (Mitsubishi, No. 12 at p. 1)
AHRI Standard 1230-2010, published after the June 2010 NOPR, duplicates
most of the requirements for tested combinations that DOE proposed in
the June 2010 NOPR except for the following requirements, which DOE
proposes in this notice to adopt to reduce manufacturer test burden:
lower the maximum number of indoor units matched to an outdoor unit;
and the option to use another indoor model family if units from the
highest sales volume model family cannot be combined so that the sum of
their nominal capacities is in the required range of the outdoor unit's
nominal capacity (between 95 and 105 percent). The proposal in June
2010 NOPR also used the term ``nominal cooling capacity,'' which may be
ambiguous; DOE also intends to clarify that such a term should be
interpreted as the highest cooling capacity listed in published product
literature for 95 [deg]F outdoor dry bulb temperature and 80 [deg]F dry
bulb, 67 [deg]F wet bulb indoor conditions, and for outdoor units as
the lowest cooling capacity listed in published product literature for
these
[[Page 69314]]
conditions. If incomplete or no operating conditions are reported, the
highest (for indoor units) or lowest (for outdoor units) such cooing
capacity shall be used. Finally, AHRI 1230 uses the term ``model
family'' but does not define the term. DOE requests comment on an
appropriate definition of ``model family'' for DOE to adopt in the
final rule. In summary, DOE proposes to omit AHRI's definition of
tested combination, found in section 3.26, from the IBR of AHRI
Standard 1230-2010 into Appendix M to Subpart B of 10 CFR part 430, and
make amendments to the proposal from the June 2010 NOPR.
During testing for ducted systems with indoor fans installed, the
rise in static pressure between the air inlet and the outlet (called
external static pressure (ESP)) must be adjusted to a prescribed
minimum that varies with system cooling capacity. The minimum ESPs are
0.10 in. wc. for units with cooling capacity less than 28,800 Btu/h;
0.15 in. wc. for units with cooling capacity from 29,000 Btu/h to
42,500 Btu/h; and 0.20 in. wc. for units with cooling capacity greater
than 43,000 Btu/h. Multi-split systems are composed of multiple indoor
units, which may be designed for installation with short-run ducts.
Such indoor units generally cannot deliver the minimum ESPs prescribed
by the current test procedure. Hence, lower minimum ESP requirements
may be necessary for testing of ducted multi-split systems.
In the June 2010 NOPR, DOE proposed lower minimum ESP requirements
for ducted multi-split systems: 0.03 in. wc. for units less than 28,800
Btu/h; 0.05 in. wc. for units between 29,000 Btu/h and 42,500 Btu/h;
and 0.07 in. wc. for units greater than 43,000 Btu/h. 75 FR at 31232.
In its comments, AHRI urged DOE to adopt the minimum ESP requirements
from AHRI Standard 1230-2010 as DOE was aware that the standard was
being developed at that time. AHRI expressed concern over the potential
abuse of lower multi-split minimum ESPs requirements by manufacturers
of ducted single-indoor-unit split-system products. Specifically, they
were concerned that the lower ESP were allowed for very specific
installation applications which could not be assured by the
manufacturer, and thus might be used more widely than intended. AHRI
therefore argued against changing ESP requirements. (AHRI, No. 6 at p.
2). Mitsubishi recommended likewise. (Mitsubishi, No. 12 at p. 2). NEEA
recommended establishing minimum ESP requirements that are the same as
those of conventional systems. (NEEA, No. 7 at p. 2) AHRI Standard
1230-2010 does not include minimum ESP requirements for multi-split
systems with short-run ducted indoor units. In order to accommodate the
design differences of these indoor units, DOE proposes to omit Table 8
of AHRI Standard 1230-2010 from the IBR into Appendix M and to set
minimum ESP requirements for systems with short-run ducted indoor units
at the levels and cooling capacity thresholds as proposed in the June
2010 NOPR. Furthermore, DOE proposes to implement these requirements by
(a) defining the term ``Short duct systems,'' to refer to ducted
systems whose indoor units can deliver no more than 0.07 in. wc. ESP
when delivering the full load air volume rate for cooling operation,
and (b) adding the NOPR-proposed minimum ESP levels to Table 3 of
Appendix M (this is the table that specifies minimum ESP), indicating
that these minimum ESPs are for short duct systems. DOE proposes using
the new term ``Short duct system'' rather than ``Multi-split system''
for these minimum ESPs because multi-circuit or mini-split systems
could potentially also include similar short-ducted indoor units. DOE
proposes a limitation in the level of ESP that eligible indoor units
can deliver in order to prevent the potential abuse of the reduced ESP
requirement mentioned by AHRI. DOE requests comment on these proposals,
including the value of maximum ESP attainable by eligible systems.
DOE notes that in conjunction with the adopted portions of the AHRI
Standard 1230-2010 , the following sections of the proposed test
procedure found in Appendix M may apply to testing VRF multi-split
systems: section 1 (definitions); section 3.12 (rounding of space
conditioning capacities for reporting purposes); sections 2.2.a, 2.2.b,
2.2.c, 2.2.1, 2.2.2, 2.2.3(a), 2.2.3(c), 2.2.4, 2.2.5, and 2.4 to 2.12
(test unit installation requirements); Table 3 in section 3.1.4.1.1c
(external static pressure requirements); section 3.1 except section
3.1.3 and 3.1.4 (general requirements of the testing procedure);
sections 3.3, 3.4, and 3.5 (procedures for cooling-mode tests);
sections 3.7, 3.8, 3.9, and 3.10 (procedures for heating-mode tests);
section 3.13 (procedure for off mode average power rating); and section
4 (calculations of seasonal performance descriptors).
DOE requests comment on the incorporation by reference of AHRI
1230-2010, and in particular the specific sections of Appendix M and
AHRI 1230-2010 that DOE proposes to apply to testing VRF systems.
3. Replacement of the Informative Guidance Table for Using the Federal
Test Procedure
The intent of the set of four tables at the beginning of ``Section
2, Testing Conditions'' of the current test procedure (10 CFR part 430,
subpart B, Appendix M) is to provide guidance to manufacturers
regarding testing conditions, testing procedures, and calculations
appropriate to a product class, system configuration, modulation
capability, and special features of products. DOE recognizes that the
current table format may be difficult to follow. Therefore, DOE has
developed a more concise table and proposes using it in place of the
current table. DOE requests comment on this proposed change and/or
whether additional modifications to the new table could be implemented
to further improve clarity.
4. Clarifying the Definition of a Mini-Split System
Current definitions in 10 CFR part 430, subpart B, Appendix M
define a mini-split air conditioner and heat pump as ``a system that
has a single outdoor section and one or more indoor sections, which
cycle on and off in unison in response to a single indoor thermostat.''
When DOE introduced this definition, mini-split systems solely employed
one or more non-ducted or short-duct wall-, ceiling-, or floor-mounted
indoor units (i.e., non-conventional units), and the market for mini-
split products reflected such type and quantity of indoor units. It was
common understanding that when testing or purchasing a mini-split
system, the system would have a non-conventional indoor unit.
Nevertheless, DOE recognizes that further clarification and
specificity in terminology would alleviate ambiguity in how to
categorize mini-split products. To differentiate the two types of
products, DOE proposes deleting the definition of mini-split air
conditioners and heat pumps, and adding two definitions for: (1)
Single-zone-multiple-coil split-system, representing a split-system
that has one outdoor unit and that has two or more coil-only or blower
coil indoor units connected with a single refrigeration circuit, where
the indoor units operate in unison in response to a single indoor
thermostat; and (2) single-split-system, representing a split-system
that has one outdoor unit and that has one coil-only or blower coil
indoor unit connected to its other component(s) with a single
refrigeration circuit. DOE seeks comment on this proposal.
[[Page 69315]]
5. Clarifying the Definition of a Multi-Split System
A multiple-split (or multi-split) system is currently defined in 10
CFR part 430, subpart B, Appendix M as ``a split-system having two or
more indoor units, which respond to multiple thermostats.''
Technologies exist on the market that operate like multi-split systems
but incorporate multiple outdoor units into the same package. To
clearly define what arrangement qualifies as a multi-split system, DOE
proposes to clarify the definition of multi-split system to specify
that multi-split systems are to have only one outdoor unit. (DOE notes
that it proposes to separately define multi-circuit units as units that
incorporate multiple outdoor units into the same package. This is
discussed in section III.C.2.) Finally, DOE proposes to clarify that if
a model of outdoor unit could be used both for single-zone-multiple-
coil split-systems and for multi-split-systems, it should be tested as
a multi-split system.
G. Test Procedure Reprint
The test procedure changes proposed in this SNOPR as well as in the
June 2010 NOPR, April 2011 SNOPR, and October 2011 SNOPR occur
throughout large portions of Appendix M to 10 CFR part 430 Subpart B.
In order to improve clarity regarding the proposed test procedure, in
the regulatory text for this SNOPR, DOE has reprinted the entirety of
Appendix M, including all changes proposed in this SNOPR as well as
those in the previous NOPR and SNOPRs that are still applicable. Table
III.6 lists those proposals from the previous notices that appear
without modification in this regulatory text reprint, and provides
reference to the respective revised section(s) in the regulatory text.
Table III.7 lists those proposals from the previous notices that either
are proposed to be withdrawn or amended in this SNOPR or propose no
amendments to the test procedure, and provides reference to the
respective preamble section for the discussion of the revision,
including stakeholder comments from the original proposal, and the
revised section(s) in the regulatory text, if any. The proposed
amendments to Appendix M would not change the rated values.
Because Appendix M1, as discussed in I.A, is substantially similar
to Appendix M, DOE is only printing the proposed regulatory text for
Appendix M1 where it differs from the proposed regulatory text for
Appendix M. Proposed changes relevant to Appendix M1 are discussed in
section III.H.
Table III.6--Proposals From Prior Notices Adopted Without Modification in This SNOPR
----------------------------------------------------------------------------------------------------------------
Proposal to . . . Preamble Regulatory text
Section Reference Action discussion location *
----------------------------------------------------------------------------------------------------------------
June 2010 NOPR
----------------------------------------------------------------------------------------------------------------
A.7............... Add Calculations 75 FR 31229...... Upheld........... III.I.5.......... 3.3c, 4.6.
for Sensible
Heat Ratio.
A.10.............. Add Definitions 75 FR 31231...... Upheld........... None............. Definitions.
Terms Regarding
Standby Power.
B.4............... Allow a Wider 75 FR 31233...... Upheld........... None............. 3.1.4.1.1a.4b.
Tolerance on Air
Volume Rate To
Yield More
Repeatable
Laboratory
Setups.
B.5............... Change the 75 FR 31234...... Upheld........... None............. 3.3d Table, 3.5h
Magnitude of the Table, 3.7a
Test Operating Table, 3.8.1
Tolerance Table, 3.9f
Specified for Table.
the External
Resistance to
Airflow.
Change the 75 FR 31234...... Upheld........... None............. 3.3d Table, 3.5h
Magnitude of the Table, 3.7a
Test Operating Table, 3.8.1
Tolerance Table.
Specified for
the Nozzle
Pressure Drop.
B.6............... Modify 75 FR 31234...... Upheld........... III.E.7.......... 2.2.5.
Refrigerant
Charging
Procedures:
Disallow Charge
Manipulation
after the
Initial Charge.
B.7............... Require All Tests 75 FR 31235, Upheld........... III.F.1.......... 2.2.5.8.
be Performed 31250.
with the Same
Refrigerant
Charge Amount.
B.8............... When Determining 75 FR 31235...... Upheld........... None............. 3.4c, 3.5i,
the Cyclic 3.7e, 3.8.
Degradation
Coefficient CD,
Correct the
Indoor-Side
Temperature
Sensors Used
During the
Cyclic Test To
Align With the
Temperature
Sensors Used
During the
Companion Steady-
State Test, If
Applicable:
Equation.
When Determining 75 FR 31236...... Upheld........... None............. 3.3b, 3.7a,
the Cyclic 3.9e, 3.11.1.1,
Degradation 3.11.1.3,
Coefficient CD, 3.11.2a.
Correct the
Indoor-Side
Temperature
Sensors Used
During the
Cyclic Test To
Align With the
Temperature
Sensors Used
During the
Companion Steady-
State Test, If
Applicable:
Sampling Rate.
B.9............... Clarify Inputs 75 FR 31236...... Upheld........... None............. 3.9.2a.
for the Demand
Defrost Credit
Equation.
B.10.............. Add Calculations 75 FR 31237...... Upheld........... III.I.5.......... 3.3c, 4.6.
for Sensible
Heat Ratio.
B.11.............. Incorporate 75 FR 31237...... Upheld........... III.C.3.......... 2.2.3, 2.2.3b,
Changes To Cover 2.4.1b,
Testing and 3.1.4.1.1d,
Rating of Ducted 3.1.4.2e,
Systems Having 3.1.4.4.2d,
More Than One 3.1.4.5.2f,
Indoor Blower. 3.2.2, 3.2.2.1,
3.6.2, 3.2.6,
3.6.7, 4.1.5,
4.1.5.1,
4.1.5.2, 4.2.7,
4.2.7.1,
4.2.7.2,
3.2.2.2 Table,
3.6.2 Table.
B.12.............. Add Changes To 75 FR 31238...... Upheld........... III.C.4.......... 3.6.6, 4.2.6.
Cover Triple-
Capacity,
Northern Heat
Pumps.
B.13.............. Specify 75 FR 31238...... Upheld........... III.F.1.......... 2.2d.
Requirements for
the Low-Voltage
Transformer Used
When Testing for
Off-Mode Power
Consumption.
[[Page 69316]]
B.14.............. Add Testing 75 FR 31238...... Upheld........... III.D............ Definitions,
Procedures and 3.13, 4.3, 4.4.
Calculations for
Off Mode Power
Consumption.
----------------------------------------------------------------------------------------------------------------
April 2011 SNOPR
----------------------------------------------------------------------------------------------------------------
III.A............. Revise Test 76 FR 18107...... Upheld........... III.D............ Definitions,
Methods and 3.13, 4.3, 4.4.
Calculations for
Off-Mode Power
and Energy
Consumption.
III.B............. Revise 76 FR 18109...... Upheld........... III.F.1.......... 2.2d.
Requirements for
Selecting the
Low-Voltage
Transformer Used
During Off-Mode
Test(s).
III.D............. Add Calculation 76 FR 18111...... Upheld........... None............. 4.7.
of the Energy
Efficiency Ratio
for Cooling Mode
Steady-State
Tests.
III.E............. Revise Off-Mode 75 FR 31238...... Upheld........... III.D............ Definitions,
Performance 3.13, 4.3, 4.4.
Ratings.
----------------------------------------------------------------------------------------------------------------
October 2011 SNOPR
----------------------------------------------------------------------------------------------------------------
III.A............. Reduce Testing 76 FR 65618...... Upheld........... III.D............ Definitions,
Burden and 3.13, 4.3, 4.4.
Complexity.
III.B............. Add Provisions 76 FR 65619...... Upheld........... III.D............ Definitions,
for Individual 3.13, 4.3, 4.4.
Component
Testing.
III.C............. Add Provisions 76 FR 65620...... Upheld........... III.D............ Definitions,
for Length of 3.13, 4.3, 4.4.
Shoulder and
Heating Seasons.
III.D............. Revise Test 76 FR 65620...... Upheld........... III.D............ Definitions,
Methods and 3.13, 4.3, 4.4.
Calculations for
Off-Mode Power
and Energy
Consumption.
III.D.1........... Add Provisions 76 FR 65621...... Upheld........... III.D............ Definitions,
for Large 3.13, 4.3, 4.4.
Tonnage Systems.
III.D.2........... Add Requirements 76 FR 65622...... Upheld........... III.D............ Definitions,
for Multi- 3.13, 4.3, 4.4.
Compressor
Systems.
----------------------------------------------------------------------------------------------------------------
* Section numbers in this column refer to the proposed Appendix M test procedure in this notice.
Table III.7--Proposals From Prior Notices Withdrawn or Amended in This SNOPR or Proposed No Change to the Test
Procedure
----------------------------------------------------------------------------------------------------------------
Proposal to . . . Preamble Regulatory text
Section Reference Action discussion location *
----------------------------------------------------------------------------------------------------------------
June 2010 NOPR
----------------------------------------------------------------------------------------------------------------
A.1............... Set a Schedule 75 FR 31227...... No Change **..... None............. None.
for Coordinating
the Publication
of the Test
Procedure and
Energy
Conservation
Standards.
A.2............... Bench Testing of 75 FR 31227...... No Change **..... None............. None.
Third-Party
Coils.
A.3............... No Change to 75 FR 31227...... Amended.......... III.H.3.......... 10 CFR Part 430,
Default Values Subpart B,
for Fan Power. Appendix M1
3.3d, 3.5.1,
3.7c, 3.9.1b.
A.4............... No Change to 75 FR 31228...... Amended.......... III.H.1.......... 10 CFR Part 430,
External Static Subpart B,
Pressure Values. Appendix M1
3.1.4.1.1c.
Table.
A.5............... No Conversion to 75 FR 31228...... No Change **..... III.I.4.......... None.
Wet-Coil Cyclic
Testing.
A.6............... No Change to Test 75 FR 31229...... No Change **..... None............. None.
Procedure for
Testing Systems
with ``Inverter-
Driven
Compressor
Technology''.
A.8............... Regional Rating 75 FR 31229...... Withdrawn None............. None.
Procedure. [dagger].
A.9............... Modify Definition 75 FR 31230...... Amended.......... III.F.2.......... 10 CFR 430.2
of Tested Definitions.
Combination.
Add Minimum ESP 75 FR 31230...... Amended.......... III.F.2.......... 3.1.4.1.1c.
for Short Duct Table.
Systems.
Clarify That 75 FR 31230...... Withdrawn None............. None.
Optional Tests [dagger].
May Be Conducted
without
Forfeiting Use
of the Default
Value(s).
B.1............... Modify the 75 FR 31231...... Amended.......... III.F.2.......... 10 CFR 430.2
Definition of Definitions.
``Tested
Combination''.
B.2............... Add Minimum ESP 75 FR 31232...... Amended.......... III.F.2.......... 3.1.4.1.1c.
for Short Duct Table.
Systems.
Add Indoor Unit 75 FR 31232...... Amended.......... III.F.2.......... 3.1.4.1.1c.
Design Table header.
Characteristics
for Limiting
Application of
Minimum ESP for
Short Duct
Systems.
B.3............... Clarify That 75 FR 31233...... Withdrawn None............. None.
Optional Tests [dagger].
May Be Conducted
Without
Forfeiting Use
of the Default
Value(s).
B.6............... No Adoption of 75 FR 31234...... No Change **..... None............. None.
Requirement of
Manufacturer
Sign-Off after
Charging
Refrigerant.
B.7............... Allow 75 FR 31235...... Withdrawn........ III.F............ None.
Interactions
between
Manufacturers
and Third-Party
Testing
Laboratory.
[[Page 69317]]
B.15.............. Add Parameters 75 FR 31239...... Withdrawn None............. None.
for Establishing [dagger].
Regional
Standards.
B.15a............. Use a Bin Method 75 FR 31240...... Withdrawn None............. None.
for Single-Speed [dagger].
SEER
Calculations for
the Hot-Dry
Region and
National Rating.
B.15b............. Add New Hot-Dry 75 FR 31240...... Withdrawn None............. None.
Region Bin Data. [dagger].
B.15c............. Add Optional 75 FR 31241...... Withdrawn None............. None.
Testing at the A [dagger].
and B Test
Conditions With
the Unit in a
Hot-Dry Region
Setup.
B.15d............. Add a New 75 FR 31242...... Withdrawn None............. None.
Equation for [dagger].
Building Load
Line in the Hot-
Dry Region.
B.16.............. Add References to 75 FR 31243...... Withdrawn........ III.E.13......... None.
ASHRAE 116-1995
for Equations
That Calculate
SEER and HSPF
for Variable
Speed Systems.
B.17.............. Update Test 75 FR 31243...... Amended.......... III.E.12......... 10 CFR 430.3
Procedure Definitions.
References.
----------------------------------------------------------------------------------------------------------------
April 2011 SNOPR
----------------------------------------------------------------------------------------------------------------
III.C............. Withdraw of the 76 FR 18110...... No Change **..... None............. None.
Proposal To Add
the New Regional
Performance
Metric SEER Hot-
Dry.
----------------------------------------------------------------------------------------------------------------
October 2011 SNOPR
----------------------------------------------------------------------------------------------------------------
Proposals are Upheld
----------------------------------------------------------------------------------------------------------------
* Section numbers in this column refer to the proposed Appendix M test procedure in this Notice, unless
otherwise specified.
** These items were discussed in the NOPR or SNOPR but did not propose changes to the test procedure.
[dagger] Associated proposals regarding the SEER Hot-Dry metric, as indicated, are withdrawn because DOE
withdrew the SEER Hot-Dry metric in the April 2011 SNOPR. 76 FR 18110.
H. Improving Field Representativeness of the Test Procedure
DOE received comments from stakeholders during the public comment
period following the November 2014 ECS RFI requesting changes to the
test procedure that would improve field representativeness. Such
changes would impact the rated efficiency of central air conditioners
and heat pumps. As discussed in section I.A, any amendments proposed in
this SNOPR that would alter the measured efficiency, as represented in
the regulating metrics of EER, SEER, and HSPF, are proposed as part of
a new Appendix M1 to Subpart B of 10 CFR part 430. The test procedure
changes proposed as part of a new Appendix M1, if adopted, would not
become mandatory until the existing energy conservation standards are
revised to account for the changes to rated values. (42 U.S.C.
6293(e)(2)) These changes, including the relevant stakeholder comments,
are discussed in the following subsections.
1. Minimum External Static Pressure Requirements for Conventional
Central Air Conditioners and Heat Pumps
Most of the central air conditioners and heat pumps used in the
United States use ductwork to distribute air in a residence, using
either a fan inside the indoor unit or housed in a separate component,
such as a furnace, to move the air. External static pressure (ESP) for
a central air conditioner or heat pump is the static pressure rise
between the inlet and outlet of the indoor unit that is needed to
overcome frictional losses in the ductwork. The ESP imposed by the
ductwork affects the power consumed by the indoor blower, and therefore
also affects the SEER and/or HSPF of a central air conditioner or heat
pump.
The current DOE test procedure \22\ stipulates that certification
tests for central air conditioners and heat pumps which are not short
duct systems (see section III.F.2) or small-duct, high-velocity systems
\23\ (i.e., conventional central air conditioners and heat pumps) must
be performed with an ESP at or above 0.10 in. wc. if cooling capacity
is rated at 28,800 Btu/h or less; at or above 0.15 in. wc. if cooling
capacity is rated from 29,000 Btu/h to 42,500 Btu/h; and at or above
0.20 in. wc. if cooling capacity is rated at 43,000 Btu/h or more.
---------------------------------------------------------------------------
\22\ Table 3 of 10 CFR 430 Subpart B Appendix M
\23\ 10 CFR 430 Subpart B Appendix M Section 1. Definitions
defines a small-duct, high-velocity system as a system that contains
a blower and indoor coil combination that is designed for, and
produces, at least 1.2 inches (of water) of external static pressure
when operated at the full-load air volume rate of 220-350 cfm per
rated ton of cooling. When applied in the field, small-duct products
use high-velocity room outlets (i.e., generally greater than 1000
fpm) having less than 6.0 square inches of free area.
---------------------------------------------------------------------------
DOE decided in the June 2010 NOPR not to propose revisions to
minimum external static pressure requirements, stating that new values
and a consensus standard were not readily available. 75 FR 13223, 31228
(June 2, 2010). NEEA responded during the subsequent public comment
period that current ESP minimums were too low and recommended DOE adopt
an ESP test requirement of 0.5 in. wc. (NEEA, No. 7 at p. 3).
Earthjustice commented that retention of the existing ESP values is not
supported by evidence. (Earthjustice, No. 15 at pp. 1-2). Southern
California Edison (SCE), the Southern California Gas Company (SCGC),
and San Diego Gas and Electric (SDGE) (together, the Joint California
Utilities) included with its comments two studies showing field
measurements of ESP with an average of 0.5-0.8 in. w.c and urged the
Department to adopt an external static pressure test point of 0.5 in.
wc. (Joint California Utilities, No. 9 at p. 3). ACEEE suggested that
field data is available for DOE to consider new values of ESP. (ACEEE,
No. 8 at pp. 2-3).
Stakeholders also commented in response to the November 2014 ECS
RFI that the current requirements for minimum ESP are unrepresentative
of field practice. PG&E commented that the ESP for central air
conditioners and heat pumps needs to be set at 0.5 in. wc. or
[[Page 69318]]
higher for ducted systems. (Docket No. EERE-2014-BT-STD-0048, PG&E, No.
15 at p. 3) ACEEE advocated similarly: Default ESP used in the current
federal test procedure should be raised from the current 0.1 to 0.2 in.
wc. to at least 0.5 in. wc. to represent field practice. (Id.; ACEEE,
No. 21 at p. 2) ASAP & ASE & NRDC commented that the ESP in the current
test procedure is unrealistically low, adding that DOE should reference
to the ESP values adopted by the recently finalized furnace fan
rulemaking which has an ESP value of 0.5 in. wc.\24\ (Id.; ASAP & ASE &
NRDC, No. 20 at p. 1).
---------------------------------------------------------------------------
\24\ Docket No. EERE-2010-BT-TP-0010-0043.
---------------------------------------------------------------------------
Central air conditioners and heat pumps are generally equipped with
air filters when used in the field. Section 3.1.4.1.1c of 10 CFR part
430, subpart B, Appendix M requires that any unit tested without an air
filter installed be tested with ESP increased by 0.08 in. wc. to
represent the filter pressure drop. University of Alabama commented
during the public comment period of the November 2014 ECS RFI that the
actual combined ESP requirements in the field are typically 3 to 5
times greater with more effective filters and typical duct designs. The
unrealistically low rating conditions result in little incentive for
manufacturers to incorporate improved fan wheel designs. Improvements
in SEER gained by replacing inexpensive forward-curve fan wheels will
be negligible but demand and energy savings in actual installations
will be significant. (Docket No. EERE-2014-BT-STD-0048, University of
Alabama, No. 6 at p. 1).
Furnaces use the same ductwork as central air conditioners and heat
pumps to distribute air in a residence. NEEA & NPCC commented that the
ESP selected for testing of furnace fans is substantially higher than
the 0.1 to 0.2 in. wc. prescribed by the federal CAC/HP test procedure.
They also mentioned that field data from Pacific Northwest shows that
the minimum required ESP is 0.5 in. wc. regardless of system capacity.
NEEA & NPCC recommended that the ESP requirement for measurement of
cooling efficiency be close to 0.6 in. wc. because air volume rates for
cooling (and heating for heat pumps) are greater than typical furnace
heating air volume rates. However, they suggested DOE adopt the ESP
level required for testing of furnace fans as a simple approach.
(Docket No. EERE-2014-BT-STD-0048, NEEA & NPCC, No. 19 at p. 2).
In response to stakeholder comment over multiple public meetings
that the minimum ESP values intended for testing are indeed
unrepresentative of the ESPs in field installations, and field studies
indeed demonstrating the same, DOE proposes in this SNOPR revising the
ESP requirements for most central air conditioners and heat pumps,
e.g., those that do not meet the proposed requirements for short duct
systems or the established requirements for small-duct, high-velocity
(SDHV) systems.
DOE is not considering revising the minimum ESP requirement for
SDHV systems. DOE is, however, proposing to establish a new category of
ducted systems, short duct systems, which would have lower ESP
requirements for testing--this is discussed in section III.F.2.
To meet the requirement set forth in 42 U.S.C. 6293(b)(3) providing
that test procedures be reasonably designed to produce test results
which measure energy efficiency of a covered product during a
representative average period of use, DOE reviewed available field data
to determine appropriate ESP values. DOE gathered field studies and
research reports, where publically available, to estimate field ESPs.
DOE previously reviewed most of these studies when developing test
requirements for furnace fans. The 20 studies, published from 1995 to
2007, provided 1,010 assessments of location and construction
characteristics of central air conditioner or heat pump systems in
residences, with the data collected varying by location, representation
of system static pressure measurements, and equipment's age and
ductwork arrangement, vintage, and air-tightness. 79 FR 500 (Jan. 3,
2014). DOE observed measured ESPs to range from 0.20 to 0.70 in. wc.
DOE used three statistical approaches to determine an average
representation of ESP from the range of ESPs: a simple-average
approach, a sample-size-exclusion approach, and a most-samples
approach. DOE then performed reconciliation, through equal weighting of
the results from the three approaches, to obtain a ``middle ground''
value of 0.32 in. wc. as the ESP representing a typical residence with
a new space conditioning system.
DOE is aware that units used in certification laboratory testing
have not aged and are thus not representative of seasoned systems in
the field. Namely, dust, dander, and other airborne particulates,
commonly deposited as foulant onto in-duct components in field
installations, are unaccounted for in controlled testing environments.
Foulant fills air gaps of the air filter and evaporator coil and
restricts air volume rate, thus increasing ESP. This occurrence is not
accounted for in certification testing environments. Therefore, DOE
included an ESP adder for component foulant build-up to the test
procedure to better reflect a representative average period of use. To
determine the value of this adder, DOE examined the aforementioned
field studies that captured the ESP contribution from vintage, and
certainly fouled, air filters and evaporator coils. From the
contributing studies, DOE estimates an average pressure drop due to the
filter's foulant of 0.13 in. wc. based on the difference in static
pressure contributions between fouled filters and clean filters. DOE
also examined publicly available reference material and research to
determine the pressure drop from the build-up of foulant on evaporator
coils. Three resources in the public domain were identified that
documented the impact of evaporator coil fouling on ESP in
applications.\25\ From this literature, DOE estimates an average
pressure drop resulting from evaporator coil fouling of 0.07 in. wc.
These additional pressure drops result in a total of 0.20 in. wc. being
added to the revised ESP value, as mentioned. DOE seeks comment on its
proposal to include in the ESP requirement a pressure drop contribution
associated with average typical filter and indoor coil fouling levels
and its use of residential-based indoor coil and filter fouling
pressure drop data to estimate the appropriate ESP contribution. DOE
also requests any data that would validate the proposed ESP
contributions or suggestions of adjustments that should be made to
improve representativeness of the values in this proposal. DOE notes
that addition of these pressure drop contributions is consistent with
the approach adopted for testing of furnace fans, which are tested
without the filter and air conditioning coil, and for which the ESP
selected for testing reflects the field fouling associated with these
components.
---------------------------------------------------------------------------
\25\ Siegel, J., Walker, I., and Sherman, M. 2002. ``Dirty Air
Conditioners: Energy Implications of Coil Fouling'' Lawrence
Berkeley National Laboratory report, number LBNL-49757.
ACCA. 1995. Manual D: Duct Systems. Washington, DC, Air
Conditioning Contractors of America.
Parker, D. S., J. R. Sherwin, et al. 1997. ``Impact of
evaporator coil airflow in air conditioning systems'' ASHRAE
Transactions 103(2): 395-405.
---------------------------------------------------------------------------
Consistent with the current motivation in current certification
procedures to promulgate policy that represents the majority of
products in the field (10 CFR 429.16(a)(2)(ii)), DOE selected the
capacity with the largest volume of retail sales, 3 tons, as the rated
cooling capacity category to adopt
[[Page 69319]]
the minimum ESP requirement based on the field data and the
adjustments. For the other cooling capacity categories, NEEA commented
that ESP should not vary with capacity. (NEEA, No. 7 at p. 3). DOE
considered the stakeholder comment and the higher ESPs indicative of
larger homes, and proposes a compromise approach to use the current
0.05 in. wc. step variation among capacities.
In conclusion, DOE proposes to adopt, for inclusion into 10 CFR
part 430, subpart B, Appendix M1, for systems other than multi-split
systems and small-duct, high-velocity systems, minimum ESP requirements
of 0.45 in. wc. for units with rated cooling capacity of 28,800 Btu/h
or less; 0.50 in. wc. for units with rated cooling capacity of 29,000
Btu/h or more and 42,500 Btu/h or less; and 0.55 in. wc. for units with
rated cooling capacity of 43,000 Btu/h or more. (DOE is not making such
a revision in 10 CFR part 430, subpart B, Appendix M.) The proposed
minimum ESP requirements are shown in Table III.8. DOE is aware that
such changes will impact the certification ratings SEER, HSPF, and EER
and is addressing such impact in the current energy conservation
standards rulemaking.\26\ DOE requests comment on these proposals.
---------------------------------------------------------------------------
\26\ Docket No. EERE-2014-BT-STD-0048.
Table III.8--Proposed Minimum ESP Requirements for Central Air
Conditioners and Heat Pumps Other Than Multi-Split Systems and Small-
Duct, High-Velocity Systems 27
------------------------------------------------------------------------
Minimum
Rated cooling or heating capacity (Btu/h) ESP (in.
wc.)
------------------------------------------------------------------------
Up Thru 28,800.............................................. 0.45
29,000 to 42,500............................................ 0.50
43,000 and Above............................................ 0.55
------------------------------------------------------------------------
---------------------------------------------------------------------------
\27\ DOE did not increase the ESP requirement for small-duct,
high-velocity units because the existing values in the test
procedure represent field operations.
---------------------------------------------------------------------------
2. Minimum External Static Pressure Adjustment for Blower Coil Systems
Tested With Condensing Furnaces
As discussed in section III.H.1, DOE proposes to increase the
minimum ESP required for testing blower coil central air conditioners
and heat pumps. DOE notes that there are three different blower coil
configurations: (1) An air handling unit which is a single piece of
equipment containing a blower and a coil; (2) a coil paired with a
separately-housed modular blower; (3) a coil paired with a separate
furnace. The existing federal test procedure for central air
conditioners and heat pumps does not require different minimum ESPs for
these different blower coil configurations, even though the heat
exchanger of a furnace may impose additional pressure drop on the air
stream. The additional pressure drop can contribute to higher blower
power, which may negatively affect the performance rating for a central
air conditioner. Further, condensing furnaces, which have more heat
transfer surface exposed to the flowing air than non-condensing
furnaces, may impose even more pressure drop.
Given the potential disadvantage associated with the rating of an
air conditioner with a condensing furnace as the designated air mover,
DOE proposes an adjustment to the minimum external static pressure
requirement for a rated blower coil combination using a condensing
furnace as the air mover in order to mitigate the impact on air-
conditioner ratings of furnace efficiency improvements. To aid the
selection of representative ESP adjustments, DOE conducted laboratory
testing for two condensing and three non-condensing furnaces to
determine typical furnace heat exchanger pressure drop levels. DOE
measured the pressure rise provided by each furnace when operating in
the maximum airflow-control setting at a representative air volume
rate, first as delivered and then with the furnace heat exchanger(s)
removed. DOE measured average furnace heat exchanger pressure drop
equal to 0.47 in. wc. for the condensing furnaces and 0.27 in. wc. for
the non-condensing furnaces. The data suggest that condensing furnace
pressure drop is roughly 0.2 in. wc. higher than non-condensing furnace
pressure drop. However, DOE notes that cooling operation may be at
lower air volume rates than the maximum cooling air volume rate used in
the tests, since furnaces can be paired with air-conditioners having a
range of capacities. Based on these results, DOE proposes to include in
Appendix M1 of 10 CFR part 430 Subpart B a requirement of a downward
adjustment of the required ESP equal to 0.1 in. wc. when testing an air
conditioner in a blower-coil configuration (or single-package
configuration) in which a condensing furnace is in the air flow path.
DOE is not making such a revision in 10 CFR part 430, subpart B,
Appendix M. DOE requests comments on this proposal.
3. Default Fan Power for Coil-Only Systems
The default fan power is used to represent fan power input when
testing coil-only air conditioners, which do not include their own
fans.\28\ The default was discussed in the June 2010 NOPR, in which DOE
did not propose to revise it due to uncertainty on whether higher
default values better represent field installations. 75 FR 31227 (June
2, 2010). In response to the June 2010 NOPR, Earthjustice commented
that the existing default fan power for coil-only units in the DOE test
procedure is not supported by substantial evidence. ESPs measured from
field data show significant higher values than the requirements in the
existing test procedure. (Earthjustice, No. 15 at p. 2) However, to be
consistent with the increase in ESP used for testing blower coil
products, as discussed in section III.H.1, this notice proposes
updating the default fan power (hereinafter referred to as ``the
default value'') used for testing coil-only products. DOE used
circulation blower electrical power data collected for the furnace fan
rulemaking (79 FR 38129, July 3, 2014) to determine an appropriate
default value for coil-only products.
---------------------------------------------------------------------------
\28\ See 10 CFR 430 Subpart B Appendix M section 3.3.d.
---------------------------------------------------------------------------
DOE collected circulation blower consumption data from product
literature, testing, and exchanges with manufacturers as part of the
furnace fan rulemaking. These data are often provided in product
literature in the form of tables listing air volume rate and
circulation blower electrical power input across a range of ESP for
each of the blower's airflow-control settings. DOE collected such data
for over 100 furnace fans of non-weatherized gas furnace products for
the furnace fan rulemaking. DOE used this database to calculate an
appropriate default value to represent circulation blower electrical
power for typical field operating conditions for air conditioning,
consistent with the required ESP values proposed for blower coil split-
systems. From the perspective of the furnace providing the air
movement, the ESP is higher than that required for testing blower coil
systems to account for the cooling coil and the air filter that would
be installed for a coil-only test, since furnace airflow performance is
determined without the coil and filter installed. DOE used pressure
drop associated with the filter equal to 0.08 in. wc., consistent with
the required ESP addition when testing without an air filter installed.
In addition, DOE
[[Page 69320]]
estimates that the typical pressure drop associated with an indoor coil
is 0.16 in. wc. DOE added the resulting sum, 0.24 in. wc., to the
required ESP levels for testing a blower coil system to obtain the ESP
levels it used to calculate the power input for furnaces in the furnace
fan database.
The air volume rate at which central air conditioner and heat pumps
are required to operate according to the DOE test procedure varies with
capacity. Typically, units are tested and operated in the field while
providing between 350 and 450 cfm per ton of cooling capacity. For the
purpose of determining the appropriate default value, DOE investigated
furnace fan performance at the ESP values discussed above while
providing 400 cfm per ton of cooling capacity.
A product that incorporates a furnace fan can often be paired with
one of multiple air conditioners of varying cooling capacities,
depending on the installation. For example, a non-weatherized gas
furnace model may be designed to be paired with either a 2, 3, or 4 ton
coil-only indoor unit. These combinations are possible because the
circulation blower in the furnace has multiple airflow-control
settings. Multiple airflow-control settings allow the furnace to be
configured to provide the target air volume rate for either 2, 3, or 4
ton coil-only indoor units by designating a different airflow-control
setting for cooling. For furnaces with multiple such airflow-control
settings that are suitable for air conditioning units, DOE calculated
fan power for each of these settings since they all represent valid
field operating conditions.
DOE then organized the results of the calculations by blower motor
technology used and manufacturer, averaging over both to calculate an
overall average default value. The distribution of motor technology
follows projected distribution of motors used in furnaces in the field
in the year 2021. By this time, there will be some small impact on this
distribution associated with the furnace fan rule. DOE averaged by
manufacturer based on market share.
The default fan power in the existing DOE test procedure does not
vary among different capacities. DOE maintains the same approach for
the adjusted default fan power. Using the aforementioned methodology,
DOE calculated the adjusted default fan power to be 441 W/1000 cfm and
proposes to use this value in Appendix M1 of 10 CFR part 430 Subpart B
where Appendix M included a default fan power of 365 W/1000 cfm. DOE is
not making such replacements in Appendix M of 10 CFR part 430 Subpart
B.
4. Revised Heating Load Line
In the current test procedure, the heating seasonal performance
factor (HSPF) determined for heat pumps in heating mode is calculated
by evaluating the energy usage of both the heat pump unit (reverse
refrigeration cycle) and the resistive heat component when matching the
house heating load for the range of outdoor temperatures representing
the heating season. The temperature range is split into 5-degree
``bins'', and an average temperature and total number of hours are
assigned to each bin, based on weather data for each climate region
used to represent the heating season--for the HSPF rating, this is
Region IV. The amount of heating delivered at each temperature
increases as the temperature decreases. This amount is dependent on the
size of the house that the unit is heating. In addition, there is a
relationship between the size of the house and the capacity of the heat
pump selected to heat it. For the current test procedure, the heating
load is proportional to the heating capacity of the heat pump when
operating at 47[emsp14][deg]F outdoor temperature. The heating load is
also proportional to the difference between 65[emsp14][deg]F and the
outdoor temperature. The resulting relationship between heating load
and outdoor temperature is called the heating load line--it slopes
downward from low temperatures, dropping to zero at 65[emsp14][deg]F.
The slope of the heating load line affects HSPF both by dictating the
heat pump capacity level used by two-capacity or variable-capacity heat
pumps at a given outdoor temperature, and also by changing the amount
of auxiliary electric resistance heat required when the unit's heat
pumping capacity is lower than the heating load line. The current test
procedure defines two load levels, called the minimum heating load line
and maximum heating load line. However, it is the minimum heating load
line in region IV that is used to determine HSPF for rating
purposes.\29\
---------------------------------------------------------------------------
\29\ See 10 CFR 430 Subpart B Appendix M Section 1. Definitions.
---------------------------------------------------------------------------
Studies have indicated that the current HSPF test and calculation
procedure overestimates ratings because the current minimum heating
load line is too low compared to real world situations.\30\ In response
to the November 2014 ECS RFI, NEEA and NPCC commented that the federal
test procedure does a poor job representing balance point temperatures
and electric heat energy use in the case of heat pump systems. They
pointed out the inability of the test procedure to capture dynamic
response to heating needs, such as use of electric resistance (strip)
heat during morning or afternoon temperature setup (i.e., rewarming of
the space after a thermostat setback period). They also expressed
concerns about capturing the use of electric resistance heat during
defrost cycles and at times when it shouldn't be needed, such as when
outdoor temperatures are above 30 [deg]F. (NEEA & NPCC, No. 19 at p. 2)
---------------------------------------------------------------------------
\30\ Erbs, D.G., C.E. Bullock, and R.J. Voorhis, 1986. ``New
Testing and Rating Procedures for Seasonal Performance of Heat Pumps
with Variable-Speed Compressors'', ASHRAE Transactions, Volume 92,
Part 2B.
Francisco, Paul W., Larry Palmiter, and David Baylon, 2004.
``Understanding Heating Seasonal Performance Factors for Heat
Pumps'', 2004 Proceedings of the ACEEE Summer Study on Energy
Efficiency in Buildings.
Fairey, Philip, Danny S. Parker, Bruce Wilcox, and Matthew
Lombardi, 2004. ``Climatic Impacts on Seasonal Heating Performance
Factor (HSPF) and Seasonal Energy Efficiency Ratio (SEER) for Air-
Source Heat Pumps'', ASHRAE Transactions, Volume 110, Part 2.
---------------------------------------------------------------------------
DOE agrees with NEEA and NPCC and notes that the heating balance
point determined for a typical heat pump using the current minimum
heating load line in Region IV is near 17 [deg]F, while the typical
balance point is in the range 26 to 32 [deg]F, resulting from
installing a proper sized unit based on the design cooling load
according to ACCA Manual S, 2014. The low heating balance point means
that the test procedure calculation adds in much less auxiliary heat
than would actually be needed in cooler temperatures, thus inflating
the calculated HSPF. Furthermore, the zero load point of 65 [deg]F
ambient, which is higher than the typical 50-60 [deg]F zero load
point,\31\ causes the test procedure calculation to include more hours
of operation at warmer outdoor temperatures, for which heat pump
operation requires less energy input, again inflating the calculated
HSPF. These effects result in overestimation of rated HSPF up to 30%
compared to field performance, according to a paper by the Florida
Solar Energy Center (FSEC).\32\ For these reasons, DOE reviewed the
choice of heating load line for HSPF ratings and proposes to modify it.
---------------------------------------------------------------------------
\31\ Francisco, Paul W., Larry Palmiter, and David Baylon, 2004.
``Understanding Heating Seasonal Performance Factors for Heat
Pumps'', 2004 Proceedings of the ACEEE Summer Study on Energy
Efficiency in Buildings.
\32\ Fairey, Philip, Danny S. Parker, Bruce Wilcox, and Matthew
Lombardi, 2004. ``Climatic Impacts on Seasonal Heating Performance
Factor (HSPF) and Seasonal Energy Efficiency Ratio (SEER) for Air-
Source Heat Pumps'', ASHRAE Transactions, Volume 110, Part 2.
---------------------------------------------------------------------------
[[Page 69321]]
As part of this review, ORNL conducted building load analysis using
the EnergyPlus simulation tool on a prototype residential house based
on the 2006 IECC code and summarized the study in a report to DOE.\33\
In general, the studies indicate that a heating load level closer to
the maximum load line and with a lower zero load ambient temperature is
more representative than the minimum load line presently used for HSPF
rating values.
---------------------------------------------------------------------------
\33\ ORNL, Rice, C. Keith, Bo Shen, and Som S. Shrestha, 2015.
An Analysis of Representative Heating Load Lines for Residential
HSPF Ratings, ORNL/TM-2015/281, July. (Docket No. EERE-2009-BT-TP-
0004-0046).
---------------------------------------------------------------------------
Based on the results from the ORNL studies, DOE proposes the new
heating load line equation to be used for calculation of HSPF as:
Where
[GRAPHIC] [TIFF OMITTED] TP09NO15.002
Tj = the outdoor bin temperature, [deg]F
TOD = the outdoor design temperature, [deg]F
DHR = the design heating requirement, Btu/h
Tzl = the zero load temperature, [deg]F
The proposed equation includes the following changes from the
current heating load line used for calculation of HSPF: \34\
---------------------------------------------------------------------------
\34\ Most commonly used heating load equation based on minimum
design heating requirement and region IV: Qh(47) *
0.77*(65-Tj)/60.
---------------------------------------------------------------------------
The equation form does not differ by region;
The zero load temperature varies by climate region, as
shown in Table III.6, and for Region IV is at 55 [deg]F, which is
closer to what occurs in the field;
The design heating requirement is a function of the
adjustment factor, or the slope of the heating load line, and is 1.3
rather than 0.77; and
The heating load is tied with the nominal heat pump
cooling capacity used for unit sizing rather than the heating capacity
(except for heating-only heat pumps).
Revised heating load hours were determined for the new zero load
temperatures of each climate region. The revised heating load hours are
given below in Table III.9.
Table III.9--Generalized Climatic Regional Information
----------------------------------------------------------------------------------------------------------------
Region No. I II III IV V VI
----------------------------------------------------------------------------------------------------------------
Heating Load Hours........................................ 562 909 1,363 1,701 2,202 * 1,974
Zero Load Temperature, TZL................................ 60 58 57 55 55 58
----------------------------------------------------------------------------------------------------------------
* Pacific Coast Region.
The proposed heating load line simulates the actual building load
in different climate regions, so the maximum and minimum heating load
lines of the current test procedure are not needed. The ORNL building
simulation results show that the same equation matching the building
load applies well to all regions. DOE therefore proposes eliminating
maximum and minimum DHR definitions.
DOE believes that it is more appropriate to base the heating load
line on nominal cooling capacity rather than nominal heating capacity,
because heat pumps are generally sized based on a residence's cooling
load. For the special case of heating-only heat pumps, which clearly
would be sized based on heating capacity rather than cooling capacity,
DOE proposes that the nominal heating capacity at 47 [deg]F would
replace the cooling capacity in the proposed load line equation. This
is consistent with the building heating load analysis.
The proposed altered heating load line would alter the measurement
of HSPF. DOE estimates that HSPF would be reduced on average about 16
percent for single speed heat pumps and two capacity heat pumps. The
impact on the measurement for variable-speed heat pumps is discussed in
section III.H.5. Consistent with the requirements of 42 U.S.C. 6293(e),
DOE will account for these changes in any proposed energy conservation
standard, and this test procedure proposal would not become effective
until the compliance date of any new energy conservation standard.
In response to the November 2014 ECS RFI, University of Alabama
commented that the current test procedure for central air conditioners
and heat pumps include cooling bin data at 67 [deg]F and heating bin
data at 62 [deg]F. This results in a dead band of 5 [deg]F. Because the
current test procedure prescribes the indoor temperature set point to
be 70 [deg]F for heating, and 80 [deg]F for cooling, the temperature
difference of 10 [deg]F is inconsistent with the dead band of 5 [deg]F
from the temperature bin. University of Alabama also suggested adopting
62 [deg]F and 52 [deg]F as the zero load points for cooling and heating
modes, respectively. (University of Alabama, No. 6 at p. 1-2)
The indoor dry bulb set temperature of 70 [deg]F for heating and 80
[deg]F for cooling represent field set temperature for central air
conditioners and heat pumps in a typical residential household. These
two temperatures are also used in other product or equipment classes
such as the commercial unitary air conditioners and heat pumps.\35\
---------------------------------------------------------------------------
\35\ See ANSI/AHRI Standard 340/360-2007 with Addenda 1 and 2,
Performance rating of commercial and industry unitary air-
conditioning and heat pump equipment.
---------------------------------------------------------------------------
In this notice, DOE proposes to revise the heating load line which
shifts the heating balance point and zero load point to lower ambient
temperatures. These amendments reflect more representative unit field
operations and energy use characteristics. The revised heating load
line lowers the zero load point for heating in region IV to 55 [deg]F.
Given the cooling-mode zero load point of 65 [deg]F, the proposed
change would increase the temperature difference between the heating
and cooling zero load points to 10 [deg]F, which equals the temperature
difference between cooling and heating modes thermostat set points. The
proposal would hence make these values more consistent with each other,
whether or not this consistency is necessary for accuracy of the test
procedure.
As a result of this proposed heating load line change, DOE also
proposes that cyclic testing for variable speed heat pumps be run at 47
[deg]F instead of 62 [deg]F, as required by the current test procedure
(see Appendix M, section 3.6.4 Table 11). The test would still be
[[Page 69322]]
conducted using minimum compressor speed. With the modified heating
load line there would be no heat pump operation at 62 [deg]F, so cyclic
testing at 47 [deg]F would be more appropriate. DOE seeks comment on
this proposal.
DOE proposes to make the changes to the test procedure as mentioned
in this subsection only in Appendix M1 of 10 CFR part 430 Subpart B,
and is not making such changes to Appendix M of the same Part and
Subpart.
5. Revised Heating Mode Test Procedure for Products Equipped With
Variable-Speed Compressors
A recent Bonneville Power Administration (BPA) commissioned study
done by Ecotope, Inc., and an Oak Ridge National Lab (ORNL)/Tennessee
Valley Authority (TVA) field test found the heating performance of a
variable speed heat pump, based on field data, is much lower than the
rated HSPF.\36\ Therefore, DOE revisited the heating season ratings
procedure for variable speed heat pumps, is are found in section 4.2.4
of Appendix M of 10 CFR part 430 Subpart B.
---------------------------------------------------------------------------
\36\ Larson, Ben, Bob Davis, Jeffrey Uslan, and Lucinda Gilman,
2013. Variable Capacity Heat Pump Field Study, Final Report,
Ecotope, Inc., Bonneville Power Administration, August.
Munk, J.D., Halford, C., and Jackson, R.K., 2013. Component and
System Level Research of Variable Capacity Heat Pumps, ORNL/TM-2013/
36, August.
---------------------------------------------------------------------------
The HSPF is calculated by evaluating the energy usage of both the
heat pump unit (reverse refrigeration cycle) and the resistive heat
component when matching the dwelling heating load at each outdoor bin
temperature. Currently, both the minimum and the maximum capacities are
calculated at each outdoor bin temperature to determine whether the
variable speed heat pump capacity can or cannot meet the building
heating load. At an outdoor bin temperature where the heat pump minimum
capacity is higher than the building heating load, the heat pump cycles
at minimum speed. The energy usage at such outdoor bin temperature is
determined by the energy usage of the heat pump at minimum speed and
the unit cyclic loss. At an outdoor bin temperature where the heat pump
maximum capacity is lower than the building heating load, the heat pump
operates at maximum speed. The energy usage at such outdoor bin
temperature is determined by the energy usage of the heat pump at
maximum speed and of the additional resistive heat required to meet the
building load.
In the current test procedure, the capacity and the corresponding
energy usage at minimum speeds are determined by the two minimum speed
tests at 47 [deg]F and 62 [deg]F (outdoor temperature \37\), assuming
the capacity and energy usage is linear to the outdoor temperature and
the compressor speed does not change with the outdoor temperature. The
capacity and the corresponding energy usage at maximum speeds are
determined by the two maximum speed tests at 47 [deg]F and at
17[emsp14][deg]F, assuming the compressor speed does not change with
the outdoor temperature. Both the minimum and the maximum capacities
and energy usages are also used to estimate the heat pump operating
capacity and energy usage when the heat pump operates at an
intermediate speed to match the building heating load.
---------------------------------------------------------------------------
\37\ All temperatures in section III.H.5, if not noted
otherwise, mean outdoor temperature.
---------------------------------------------------------------------------
In reviewing these calculations, DOE compared the efficiencies
(capacity divided by energy usage; at maximum speed, intermediate
speed, and minimum speed at ambient temperatures representing the
heating season) calculated using the method in current test procedure
to the efficiencies tested in the lab at each of the 5 [deg]F bin
temperatures representing the heating season, and found two
discrepancies where the efficiencies are not predicted accurately by
the test procedure.
The first discrepancy occurs only for the variable speed heat pump
that prevents minimum speed operation at outdoor temperatures below 47
[deg]F. In the mid-range outdoor temperature range (17-47 [deg]F), the
efficiencies are over-predicted. The cause of this over-prediction is
that the unit's actual minimum capacity is higher than the calculated
minimum capacity in the range of outdoor temperature 17-47 [deg]F. The
calculated minimum capacity is based on the assumption that the unit
can operate at the minimum speed in this range, which is not true with
such units.
DOE considered two alternative methods to provide more accurate
efficiency predictions for mid-range outdoor temperatures. In the first
method, the minimum capacity and the corresponding energy usage for
outdoor temperatures lower than 47 [deg]F would be determined by the
minimum speed tests at 47 [deg]F and the intermediate speed test at 35
[deg]F, which are both required test points in current test procedure.
The new calculation method results in the capacity and energy usage
more representative of the unit operation performance in the
temperature region 35-47 [deg]F. The HSPF calculated with this option
agrees with the tested HSPF within 6%. This option does not require
additional testing beyond what is required in the current test
procedure.
In the second method, the minimum capacity and the corresponding
energy usage for outdoor temperature lower than 47 [deg]F would be
determined by minimum speed tests at 47 [deg]F and at 35 [deg]F, where
the test point of minimum speed at 35 [deg]F is an additional test
point that is not required in the current test procedure. In addition,
the intermediate capacity and the corresponding energy usage would be
modified for more accurate efficiency prediction at the outdoor
temperature range 17-35 [deg]F. This is done by defining the medium
speed test as the average of the maximum and minimum speed and using
the medium speed test at 17 [deg]F and the intermediate speed test at
35 [deg]F to determine the intermediate capacity and the corresponding
energy usage, where the test at the medium speed at 17 [deg]F is a test
point not required in the current test procedure. With this method, the
unit's calculated performance is well matched with the unit's actual
operation in the outdoor temperature region 17-35 [deg]F. The HSPF
calculated with this option aligns with the tested HSPF within 2%.
However, this option requires two additional test points, medium speed
at 17 [deg]F and minimum speed at 35 [deg]F, which adds test burden for
manufacturers.
After considering these two alternative methods with regard to the
current test procedure, DOE further evaluated the impact of the
proposed heating load line change (see section III.H.4) on the variable
speed HSPF rating. DOE found that efficiencies calculated with the
modified heating load line and with the current variable speed heat
pump rating method match rather closely with those calculated from a
more detailed set of test data at each outdoor bin temperature. The
calculated HSPFs agree within 1 percent. Use of the proposed load line
greatly reduces the error in the test procedure calculation from the
speed limiting controls at ambient temperatures below 47 [deg]F. The
net effect is that the ratings calculation approach using the proposed
load line with the current test points gives results close to those
with more detailed data sets. However, because this also removes an
artificial HSPF benefit that such units were obtaining, the net
reduction in rated HSPF for such units could be as much as 26%.\38\ DOE
believes that this indicates that the modified heating load
[[Page 69323]]
line is sufficient to address the HSPF over-prediction issue for the
variable speed heat pumps. Therefore, at this time, DOE does not
propose changes specifically to the variable speed test points or
heating calculations in the proposed Appendix M1. However, DOE notes
that should stakeholder comments on this notice provide sufficient
justification to retract the proposal to adopt the proposed modified
heating load line, DOE would instead adopt, as part of Appendix M1,
modifications to the variable speed heating calculations for units that
prevent minimum speed operation. DOE requests comment on whether, in
the case that the proposed heating load line is not adopted, DOE should
modify the HSPF rating procedure for variable speed heat pumps using
option 1, which is less accurate but has no additional test burden, or
option 2, which is more accurate but with higher test burden.
---------------------------------------------------------------------------
\38\ Rice et al. (2015) Review of Test Procedure for Determining
HSPFs of Residential Variable-Speed Heat pumps. (Docket No. EERE-
2009-BT-TP-0004-0047).
---------------------------------------------------------------------------
The second potential discrepancy between the efficiencies (capacity
divided by energy usage) calculated using the method in the current
test procedure with the efficiencies tested in the lab at each outdoor
bin temperature occurs at temperatures lower than 17 [deg]F, where the
test procedure assumes the heat pump operates at the maximum speed. The
capacity and the corresponding energy usage at maximum speed at
different outdoor bin temperatures are determined by the two maximum
speed tests at 47 [deg]F and at 17 [deg]F, assuming the compressor
speed does not change with the outdoor temperature. However, DOE found
that some variable speed heat pumps do not allow maximum speed
operation when the outdoor temperature is below 17 [deg]F. For such
units, the assumption in the current test procedure is not appropriate.
The impact of this discrepancy on the HSPF is not significantly changed
by the proposed heating load line revision.
DOE proposes as part of Appendix M1 that for the variable speed
units that limit the maximum speed operation below 17 [deg]F and have a
low cutoff temperature less than 12 [deg]F, the manufacturer could
choose to calculate the maximum heating capacity and the corresponding
energy usage through two maximum speed tests at: (1) 17 [deg]F outdoor
temperature, and (2) 2 [deg]F outdoor temperature or at a low cutoff
temperature, whichever is higher.\39\ With this proposed change,
manufacturers could choose to conduct one additional steady state test,
at maximum compressor speed and at a low temperature of 2 [deg]F or at
a low cutoff temperature, whichever is higher.
---------------------------------------------------------------------------
\39\ In the case that the low cutoff temperature is higher than
12 [deg]F, the manufacturer would not be allowed to utilize this
option for calculation of the maximum heating load capacity.
---------------------------------------------------------------------------
The testing done by ORNL found that the unit efficiency at maximum
speed below 17 [deg]F is slightly higher than the extrapolated values
in the current test procedure, and this proposed option would provide a
more accurate prediction of heat pump low ambient performance not only
for those units that limit maximum speed operation below 17 [deg]F, but
also for those that do not.\40\ DOE therefore proposes to revise
Appendix M1 such that, for variable speed units that do not limit
maximum speed operation below 17 [deg]F, manufacturers would also have
the option to use this revised method if it is more representative of
low ambient performance.
---------------------------------------------------------------------------
\40\ EERE-2009-BT-TP-0004-0047.
---------------------------------------------------------------------------
DOE believes that the proposed revision reflects field energy use
more accurately. However, DOE acknowledges that the limited test
results available show very small improvements in the accuracy of the
rating method. Because the proposed revision adds an additional test
burden (one new test), DOE has proposed to make it optional rather than
mandatory. However, DOE would consider making this proposal mandatory
for some or all variable speed units, given additional information.
Specifically, DOE requests test results and other data that demonstrate
whether HSPF results for other variable speed heat pumps would be more
significantly impacted by this proposed option, as well as whether the
additional test burden would offset the advantages of the proposed
modification.
DOE notes that the proposed revision also adds additional
complexity to the test procedure in terms of which combinations of
tests need to be conducted. In the current test procedure, to calculate
the maximum speed performance in the temperature range 17-45 [deg]F,
the maximum speed performance at 35 [deg]F is required. However, the
maximum speed 35 [deg]F test is not required and performance at 35
[deg]F may instead be calculated from the two maximum speed tests at 17
[deg]F and 47 [deg]F. Therefore, even though manufacturers who choose
to rate with the optional low ambient point would no longer need the
maximum speed 47 [deg]F point to calculate energy use at maximum speed
below 17 [deg]F, they would need either the maximum speed 47 [deg]F
test point or 35 [deg]F test point to calculate the capacity and energy
use at maximum speed at 35 [deg]F. They may also wish to conduct the
maximum speed 47 [deg]F test point to rate heating capacity, although
in the proposed Appendix M1, this is only required for heating-only
heat pumps.
In summary, with the proposed option for calculating maximum speed
performance below 17 [deg]F, manufacturers would test at both maximum
speed at 2 [deg]F (or low cutoff temperature) and maximum speed at 17
[deg]F. For rating at 35 [deg]F, they would also test at either maximum
speed at 35 [deg]F or maximum speed at 47 [deg]F. Finally, to rate
heating capacity or nominal heating capacity (for units whose controls
do not allow maximum speed operation at 47 [deg]F), they may also
choose to test at either maximum speed at 47 [deg]F allowed by their
standard controls or cooling capacity maximum speed at 47 [deg]F,
respectively. Table III.10 lists the maximum speed test combination
options for the variable speed heat pumps. The test combination option
1 is the default in current test procedure.
Table III.10--Proposed Maximum Speed Heating Test Combination Options for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Test description (outdoor dry bulb Current test procedure
temperatures) (Option 1) Option 2 Option 3 Option 4 Option 5
--------------------------------------------------------------------------------------------------------------------------------------------------------
H1N (2 [deg]F)...................... optional if using ............... ....................... for nominal heating for nominal heating
nominal heating capacity. capacity.
capacity.
H12 (47 [deg]F)..................... X...................... X for heating capacity ....................... X.
only.
H22 (35 [deg]F)..................... ....................... ............... X...................... X...................... ......................
H32 (17 [deg]F)..................... X...................... X X...................... X...................... X.
[[Page 69324]]
H42 (2 [deg]F) *.................... ....................... X X...................... X...................... X.
--------------------------------------------------------------------------------------------------------------------------------------------------------
* Or low cutoff temperature, whichever is higher.
Note: For units with a low cutoff temperature higher than 12 [deg]F, options 2 through 5 are not available.
DOE additionally notes that all proposed changes in this subsection
would change the efficiency ratings of units and are therefore proposed
as part of Appendix M1 of 10 CFR 430 Subpart B. Such proposed changes
would not appear in Appendix M of the same Part and Subpart.
I. Identified Test Procedure Issues DOE may Consider in Future
Rulemakings
Various comments from stakeholders during the public comment period
following the publication of the November 2014 ECS RFI raised
additional test procedure issues. The stakeholders requested that DOE
consider these issues when amending its test procedures. After careful
consideration of these issues, DOE believes that either they cannot be
resolved or that they require additional action at this time, and
therefore declines to address them in this SNOPR. Discussion of these
test procedure issues follows in the subsequent subsections.
1. Controlling Variable Capacity Units to Field Conditions
Central air conditioners and heat pumps can be divided into single-
speed, two-capacity, or variable capacity (or speed) units based on
capacity modulation. System controls are typically more complex with
the increasing modulating capability. The DOE test procedure prescribes
different testing requirements for units depending on whether they are
single-speed, two-capacity, or variable capacity (or speed) in order to
characterize the efficiency ratings accurately.
In response to the RFI, stakeholders submitted several comments
that address the more complex operation of variable capacity central
air conditioners and heat pumps. Stakeholders also submitted comments
highlighting the need for improvement in the test procedure's ability
to accurately predict energy use in the field, even for units that do
not have variable capacity capability. PG&E urged DOE to revise the
current test procedure to reflect the more nuanced operation of modern
variable speed central air conditioners and heat pumps over the full
range of outdoor conditions, given that variable speed units operate
differently from the traditional single-speed or two-capacity units.
(PG&E, No. 15 at p. 2)
Edison Electric Institute commented that the current test procedure
for central air conditions and heat pumps need to be updated to avoid
``gaming'' of system controls to maximize rated SEER and EER, as there
is an increase in using variable speed controls for motors,
compressors, and variable refrigerant flow. (EEI, No. 18 at p. 3)
NEEA & NPCC commented that the current test procedure does not
appropriately test the operation of variable capacity systems. These
systems operate much differently in the field than the forced operating
conditions with which they are currently tested under waivers and
artificially created laboratory conditions. As a result, the efficiency
ratings and estimated energy use of these systems cannot be reliably
determined. NEEA & NPCC also claimed that the field data shows that
systems from different manufacturers with identical HSPF and SEER
ratings and identical rated capacity will use significantly different
amounts of energy under identical environmental conditions. (NEEA &
NPCC, No. 19 at p. 2) NEEA & NPCC also showed the field energy use
profiles for six units. They further commented that variable capacity
systems behave in a nearly infinite variety of ways under similar
outdoor and indoor temperature conditions, and much of this behavior
occurs outside the bounds of the test procedure conditions. (NEEA &
NPCC, No. 19 at p. 4) NEEA and NPCC commented that test procedure
updates to variable capacity equipment will have an impact on the
energy savings of these systems. They also commented that the test
procedure more accurately representing the field energy use for heat
pump systems could vary significantly by climate zone. (NEEA & NPCC,
No. 19 at p. 10)
ASAP, ASE, and NRDC commented that the current method for testing
variable-capacity units used by manufacturers who have obtained test
procedure waivers may not provide good representation of energy use in
the field or reasonable relative rankings of product. Representative
ratings of variable-capacity products will become more important in the
future as variable-capacity units become more widely adopted. (ASAP &
ASE & NRDC, No. 20 at p. 1)
PG&E commented that central air conditioners and heat pumps should
be tested at part load and cyclic testing under conditions that
represent field operations. (PG&E, No. 15 at p. 3) However, PG&E did
not provide further detail on what part load and cyclic conditions
would be field representative.
ACEEE commented that the current federal test procedure has been
awkward for rating new technologies, notably ductless equipment, and
probably some types of modulating equipment. (ACEEE, No. 21 at p. 2)
As discussed in section III.H.5, DOE proposes to amend the testing
requirements for units equipped with a variable speed compressor during
heating mode operation. These proposed amendments would improve the
field representativeness of variable speed units and better
characterize the field energy use. However, DOE acknowledges that
further improvements as suggested by the stakeholders could be possible
if more detailed field testing data is available. DOE may consider in a
future rulemaking additional amendments to improve the test procedure's
representation of field energy use. In regards to ductless and
modulating equipment, DOE's existing test procedure already covers
testing and rating of these technologies.
2. Revised Ambient Test Conditions
Central air conditioners and heat pumps operate in a wide range of
weather conditions throughout the year. Further, both the range of
temperature and humidity conditions associated with most of these
products' energy use also varies from one climate region to another.
The test procedure prescribes calculation of seasonal energy efficiency
[[Page 69325]]
metrics for cooling and heating based on a finite set of test
conditions intended to represent the range of operating conditions
while avoiding excess test burden.
DOE decided in the June 2010 NOPR not to propose modifications to
convert to wet-coil cyclic testing as data and information were not
available to quantify subsequent impacts. 75 FR 31223, 31228 (June 2,
2010). In response to the June 2010 NOPR, SCE, SCGC and SDGE submitted
a joint comment recommending DOE require that manufacturers disclose
performance data at a range of test conditions, as specified in the
Consensus Agreement. The joint comment further explained that program
designers need to know how equipment performs in a range of conditions
in order for rebate and incentive programs to be effective. This could
also make it possible for consumers to select products with performance
characteristics that meet their needs. (Docket EERE-2009-BT-TP-0004,
SCE, SCGC, and SDGE, No. 9, at p.3)
In the current AHRI certified directory,\41\ manufacturers report
the full load capacity and EER in addition to SEER for central air
conditioners. Manufacturers also report heating capacities and EERs at
both 47[emsp14][deg]F and 17[emsp14][deg]F ambient test conditions in
addition to the seasonal efficiency metric HSPF for heat pumps. Cooling
capacity and EER at full load are also reported in addition to SEER for
heat pumps. DOE believes that this rating data provides sufficient
information for determining rebate and incentive programs for program
designers.
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\41\ http://www.ahridirectory.org/ahridirectory/pages/home.aspx.
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NREL commented that the existing DOE testing and certification
requirements for central air conditioners and heat pumps do not provide
sufficient data to compare different units. NREL also urged DOE to
adopt different testing conditions for the hot dry and hot humid
region. NREL further commented that measurement of water condensation
must be reported with higher fidelity than the sensible heat ratio.
Latent loads and moisture removal should be reported in each test
condition. (EERE-2009-BT-TP-0004, NREL, No. 14 at p. 1)
DOE does not intend to establish different test conditions for
various regions of this country. DOE believes that it would add
significant burden to manufacturers to report the latent loads and
moisture removal in each test condition. In this SNOPR, DOE revises the
certification requirement to include reporting the sensible heat ratio.
See section III.I.5 for more details. DOE believes that the sensible
heat ratio provides a good indication of the moisture removal
capability for central air conditioners and heat pumps.
Stakeholders submitted a number of comments on the revised ambient
test condition in response to the RFI published on November 5, 2014. 79
FR 65603. University of Alabama commented that the testing conditions
prescribed in the federal test procedure for central air conditioners
and heat pumps are not representative of actual operation in the field.
The outdoor temperatures used for rating should be expanded from 2 to 3
for constant speed units and from 5 to 6 for multi-capacity and
variable speed units. The rating points can be used to determine more
appropriate SEER and HSPF for climates outside of the current DOE zone
4 conditions. Specifically, University of Alabama proposed the cooling
indoor dry bulb and wet bulb temperatures to be 77 [deg]F and 64.4
[deg]F, instead of the current requirement of 80 [deg]F and 67 [deg]F,
respectively. Heating indoor dry bulb temperature should use 68 [deg]F
instead of the current requirement of 70 [deg]F. For the outdoor
conditions, testing at 113 [deg]F, 95 [deg]F, and 77 [deg]F have been
proposed for the cooling mode, and 41 [deg]F, 23 [deg]F, and 5 [deg]F
have been proposed for the heating mode, respectively. (University of
Alabama, No. 6 at p. 1-2)
PG&E commented that DOE should amend the test procedure to require
testing at 76 [deg]F dry bulb with 50% relative humidity indoor
conditions to represent the comfort desired in dwellings. (PG&E, No. 15
at p. 3) However, PG&E did not provide further detail on why the
revised test condition is more representative than the requirements in
the current federal test procedure.
PG&E also commented that the current cooling condition at 95 [deg]F
does not fully capture the peak load experienced by consumers in the
hottest summer weather. PG&E further urged DOE to revise the test
procedure to account for ambient dry bulb conditions of 105 [deg]F or
115 [deg]F experienced by consumers in the desert climates. (PG&E, No.
15 at p. 3)
Moreover, PG&E commented that DOE should adopt the testing at
outdoor ambient temperatures that generate a performance map of the
system for use in annual energy use simulation. (PG&E, No. 15 at p. 3)
However, there is no further detail provided regarding this comment.
EEI suggested that DOE revise the indoor air inlet dry bulb/wet
bulb temperatures to be lowered from 80 [deg]F/67 [deg]F to 78 [deg]F/
61 [deg]F, respectively. Such a change would create more realistic
indoor conditions that would require dehumidification to ensure
properly managed indoor air quality. (EEI, No. 18 at p. 4) However, EEI
did not provide further detailed justifications why such a change would
create more realistic indoor conditions than the current federal
testing requirements.
NEEA and NPCC commented that the current federal test procedure
does not capture performance under the full range of operating
conditions for which many of these systems are designed. Some air
conditioners perform significantly better at temperatures above 100
[deg]F than others, but based on the current test procedure, there is
no testing requirement for temperatures above 95 [deg]F. For heat
pumps, systems may perform differently above 47 [deg]F and below 17
[deg]F conditions. NEEA and NPCC commented that the test procedure and
the resulting ratings should expose these differences and allow the
market to properly select the systems that are most appropriate and
most efficient for individual climate conditions. (NEEA & NPCC, No. 19
at p. 2)
ASAP, ASE, and NRDC commented that the test conditions defined in
the current test procedure do not reflect field conditions. Adding a
test point for SEER ratings at an outdoor temperature above 95 [deg]F
and adding a test point for HSPF ratings at an outdoor temperature
below 17 [deg]F would incentivize manufacturers to provide good
efficiency performance at these temperatures. In addition, requiring
reporting of performance at each of the outdoor temperature test points
would allow efficiency program administrators to incentivize equipment
that will perform well in their region. (ASAP & ASE & NRDC, No. 20 at
p. 2)
DOE appreciates that there may be value in providing more
performance data, and that the range of operating conditions in the
field may be more extensive than that represented by the current test.
However, the extensive study and test work that would have to be
conducted to properly assess and choose a better range of test
conditions has not been completed. Hence, although DOE has proposed
some changes to the test conditions required for testing of variable-
speed heat pumps in heating mode, DOE has not proposed changes as
extensive as the comments suggest. DOE may consider additional changes
addressing these issues in future test procedure rulemakings.
[[Page 69326]]
3. Performance Reporting at Certain Air Volume Flow Rates
Central air conditioners and heat pumps condition the indoor air to
satisfy cooling and heating requirements of a house. For ducted central
air conditioners and heat pumps, indoor air is driven by the blower of
the air handling unit or the furnace. Air volume rate affects the heat
transferred between the air conditioning device and indoor air, and
also affects the performance ratings of an air conditioner or heat
pump.
University of Alabama recommended that all performance results for
central air conditioners and heat pumps be reported within the air
volume rate range of 375 to 425 cfm per ton, and that the air volume
rates be included in the reporting requirements. Higher air volume
rates will result in reduced dehumidification capability and cause
thermal comfort issue. (University of Alabama, No. 9 at p. 1)
The current DOE test procedure requires that full load air volume
rate be no more than 37.5 standard cfm (scfm) per 1,000 Btu/h of
cooling capacity (see 10 CFR part 430, subpart B, Appendix M, Section
3.1.4.1.1), but the test procedure does not have a minimum air volume
rate requirement. DOE has proposed in this notice to require reporting
of the cooling full load air volume rate as part of certification
reporting. See section III.I.5 for more details. The air volume rate is
also reported in the AHRI certification database.\42\ DOE believes that
these requirements will ensure that air volume rates used for rating
central air conditioners and heat pumps are in an appropriate range.
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\42\ AHRI Directory of Certified Product Performance: https://www.ahridirectory.org/ahridirectory/pages/home.aspx.
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4. Cyclic Test With a Wet Coil
The DOE test procedure for central air conditioners and heat pumps
prescribe specific test conditions under which units are to be tested.
These test conditions include both steady-state and cyclic tests. A dry
coil test refers to the test conditions that do not result in moisture
condensing on the indoor coil, and a wet coil test refers to the test
conditions that result in moisture condensing on the indoor coil. DOE
proposed in the June 2010 NOPR not to amend the existing cyclic testing
requirement from dry coil test to wet coil test. DOE concluded that
there was no sufficient data to show a greater benefit to using wet
coil cyclic test versus the dry coil cyclic test. 75 FR 31223, 31227
(June 2, 2010).
In response to the RFI regarding central air conditioners and heat
pumps (79 FR 65603, November 5, 2014), ASAP & ASE & NRDC commented that
the cyclic test in the current test procedure is conducted using a dry
coil, which is not representative of field conditions. Using the same
indoor conditions (i.e., 80 [deg]F dry bulb and 67 [deg]F wet bulb) for
the cyclic tests as used for the steady-state test would better reflect
the cyclic performance of central air conditioners and heat pumps.
(ASAP & ASE & NRDC, No. 20 at p. 2) DOE believes this approach may have
merit, but has not sufficiently studied it to have proposed its
inclusion in the test procedure at this time. DOE may consider adopting
the approach in a future rulemaking.
5. Inclusion of the Calculation for Sensible Heating Ratio
Air conditioning reduces air temperature and also reduces humidity.
Cooling associated with air temperature reduction is called sensible
capacity, while cooling associated with dehumidification is called
latent capacity. The balance of these capacities for a given air
conditioner operating in a given set of operating conditions is
represented as sensible heat ratio (SHR), which is equal to sensible
cooling divided by total cooling. Air conditioners can be designed to
operate with high or low SHR depending on the air conditioning needs.
Similarly, an air conditioner can be optimized to maximize efficiency
depending on the indoor humidity level.
In the June 2010 NOPR, DOE proposed including the calculation for
(SHR at the B, B1, or B2 test condition (82
[deg]F dry bulb, 65 [deg]F wet bulb, outside air) in the test
procedure. 75 FR 31223, 31229 (June 2, 2010). DOE received comments
regarding the inclusion of calculations for SHR in the subsequent
public comment period. AHRI supported adoption of the SHR, provided
that it is based off the total net capacity and is a reported value
only. (AHRI, No. 6 at p. 4) Ingersoll Rand agreed with AHRI. (Ingersoll
Rand, No. 10 at pp. 2-3) Lennox likewise agreed with AHRI regarding
adding calculations for SHR and further requested that DOE provide
calculations for SHR at outdoor ambient conditions of 82 [deg]F.
(Lennox, No. 11 at p. 1) Building Science Corporation stated that the
calculation of the SHR was a favorable step towards inclusion of a
dehumidification performance rating, but requested determining SHR at
multiple outdoor and indoor conditions and reporting a metric for
moisture removal efficacy. (Building Science Corporation, No. 16 at p.
1) NEEA concurred with DOE's proposal in the NOPR to add calculations
of sensible heat ratio (SHR) to the test procedure requirements. (NEEA,
No. 7 at p. 6) The People's Republic of China World Trade Organization
Technical Barriers to Trade National Notification and Enquiry Center
(China WTO) suggested that SHR be calculated at the same SEER test
conditions. (China WTO, No. 18 at p. 4).
DOE does not believe that measurements at multiple indoor or
outdoor conditions are necessary to obtain a SHR value that represents
unit operation during an average use cycle or period. (42 U.S.C.
6293(b)(3)) Therefore, DOE is maintaining its position in the NOPR to
include calculation for sensible heat ratio at only the condition at
which products are rated (82 [deg]F dry bulb, 65 [emsp14][deg]F wet
bulb, outside air), and proposes to include this change to the revised
Appendix M test procedure in this notice. DOE notes that the addition
of these calculations does not add significant test burden because the
existing measurement instruments, used for determining the inputs for
SEER, can also determine the inputs for SHR.
The June 2010 NOPR highlighted a Joint Utilities recommendation
that DOE should require all units be certified and rated for sensible
heat ratio (SHR) at 82 [deg]F ambient dry bulb temperature. 75 FR
31223, 31229 (June 2, 2010). DOE believes that the existing
certification test procedures and ratings are sufficient to determine
product efficiency; efforts to establish dehumidification performance
for central air conditioner and heat pumps are not currently necessary
given that the primary function of the subject products is not
dehumidification, nor would doing so be helpful in improving the
accuracy of product efficiency.
In response to the RFI regarding central air conditioners and heat
pumps (79 FR 65603, November 5, 2014), stakeholders submitted several
comments on the reporting requirements related to the SHR. PG&E
commented that the test procedure should adopt testing that
characterizes the sensible heat ratios for high (western dry climates,
approximately 500 cfm/ton) and low (eastern humid climates,
approximately 350 cfm/ton) evaporator coil air volume rate. (Docket No.
EERE-2014-BT-STD-0048, PG&E, No. 15 at p. 3) Edison Electric Institute
commented that the test procedure should take into account a
dehumidification requirement as homes are getting tighter with fewer
air changes. (Id.; EEI, No. 18 at p. 3) ASAP & ASE & NRDC requested DOE
require reporting sensible heat ratio for central air conditioners and
heat pumps. Sensible heat ratio would provide more
[[Page 69327]]
information to consumers and contractors about appropriate units for
their region and also allow efficiency program administrators to better
target efficiency programs for central air conditioners and heat pumps.
(Id.; ASAP & ASE & NRDC, No. 20 at p. 2)
In response to the stakeholder comments, DOE understands that air
volume rate can be controlled properly to suit the dehumidification
purposes. However, manufacturers can design their products to meet the
needs of consumers in different climate regions. Therefore, DOE does
not intend at this time to develop a test procedure that requires
different air volume rates based on the climate region. DOE does,
however, realize the merit of reporting SHR for consumer choices. As
such, DOE proposes to simply require the reporting of the SHR value
calculated based on full-load cooling test conditions at the outdoor
ambient conditions proposed earlier in this section: 82 [deg]F dry bulb
and 65 [deg]F wet bulb.
J. Compliance With Other Energy Policy and Conservation Act
Requirements
1. Test Burden
EPCA requires that any test procedures prescribed or amended shall
be reasonably designed to produce test results which measure energy
efficiency, energy use, or estimated annual operating cost of a covered
product during a representative average use cycle or period of use, and
shall not be unduly burdensome to conduct. (42 U.S.C. 6293(b)(3)) For
the reasons that follow, DOE has tentatively concluded that revising
the DOE test procedure, per the proposals in this SNOPR, to measure the
energy consumption of central air conditioners and heat pumps in active
mode and off mode would produce the required test results and would not
result in any undue burdens.
As discussed in section IV.B of this SNOPR, the proposed test
procedures to determine the active-mode and standby-mode energy use
would require use of the same testing equipment and facilities that
manufacturers are currently using for testing to determine CAC and CHP
ratings for certifying performance to DOE. While this notice proposes
clarifications to the test procedures, and proposes adopting into
regulation the test procedures associated with a number of test
procedure waivers, most of the proposals would not affect test time or
the equipment and facilities required to conduct testing. Possible
changes in test burden associated with the proposals of this notice
apply to off mode testing and requirements for testing of basic models
by ICMs.
The proposals include additional testing to determine off mode
energy use, as required by EPCA. (42 U.S.C. 6295(gg)(2)(A)) This
additional testing may require investment in additional temperature-
controlled facilities. However, DOE's proposal does not require that
every individual combination be tested for off mode, allowing
sufficient use of AEDMs in order to reduce test burden.
The proposals also call for testing to determine performance for
ICMs. Specifically, the proposals call for testing of one split system
combination for each model of indoor unit sold by an ICM. While this
change would increase test burden for these manufacturers, DOE believes
it is the appropriate minimum test burden to validate ratings for these
systems, as it is consistent with current requirements for OUMs, for
which testing is required for every model of outdoor unit. DOE requests
comment on this issue.
DOE allows manufacturers to pursue an alternative efficiency
determination method process to certify products without the need of
testing. In this notice, DOE revises and clarifies such requirements,
as detailed in section III.B, to continue to enable manufacturers who
wish to reduce testing burden to utilize this method.
As detailed in section III.C, manufacturers of certain products
covered by test procedures waivers, have already utilized the
alternative test procedures provided to them for certification testing.
Thus, the inclusion of said alternative test procedures into the test
procedure, as revised in this notice, does not add additional test
burden.
In addition, DOE carefully considered the testing burden on
manufacturers in proposing a modified off mode test procedure that is
less burdensome than the proposals it made in the April 2011 SNOPR and
October 2011 SNOPR and that addresses stakeholder comment regarding the
test burden of such prior proposals. Further discussion regarding test
burden associated with the proposals set forth in this notice for
determining off mode power consumption can be found in section III.D.
DOE set forth proposals to improve test repeatability, improve the
readability and clarity of the test procedure, and utilize industry
procedures that manufacturers may be aware of in an effort to reduce
the test burden. Sections III.E, III.F, and III.G presents additional
detail regarding such proposals.
Although DOE proposes to change the current test procedure in a
manner that would impact measured energy efficiency, amend existing
requirements, and increase the testing time for such tests, DOE
carefully considered the impact on testing burden and made efforts to
balance accuracy, repeatability, and test burden during the course of
the development of such proposals. Further discussion is found in
section III.H.
Therefore, DOE determined that the proposed revisions to the
central air conditioner and heat pump test procedure would produce test
results that measure energy consumption during a period of
representative use, and that the test procedure would not be unduly
burdensome to conduct.
2. Potential Incorporation of International Electrotechnical Commission
Standard 62301 and International Electrotechnical Commission Standard
62087
Under 42 U.S.C. 6295(gg)(2)(B), EPCA directs DOE to consider IEC
Standard 62301 and IEC Standard 62087 when amending test procedures for
covered products to include standby mode and off mode power
measurements.
DOE reviewed IEC Standard 62301, ``Household electrical
appliances--Measurement of standby power'' (Edition 2.0 2011-01),\43\
and determined that the procedures contained therein for preparation of
the unit under test and for conducting the test are already set forth
in the amended test procedure, as proposed in this notice, for
determining off mode power consumption and for determining the
components (cyclic degradation coefficient) that make up standby power
for central air conditioners and heat pumps. Therefore, DOE determined
that referencing IEC Standard 62301 is not necessary for the proposed
test procedure that is the subject of this rulemaking.
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\43\ IEC Standard 62301 covers measurement of power consumption
for standby mode and low power modes, as defined therein.
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DOE reviewed IEC Standard 62087, ``Methods of measurement for the
power consumption of audio, video, and related equipment'' (Edition 3.0
2011-04), and determined that it would not be applicable to measuring
power consumption of HVAC products such as central air conditioners and
heat pumps. Therefore, DOE determined that referencing IEC Standard
62087 is not necessary for the proposed test procedure that is the
subject of this rulemaking.
[[Page 69328]]
IV. Procedural Issues and Regulatory Review
A. Review Under Executive Order 12866
The Office of Management and Budget (OMB) has determined that test
procedure rulemakings do not constitute ``significant regulatory
actions'' under section 3(f) of Executive Order 12866, Regulatory
Planning and Review, 58 FR 51735 (Oct. 4, 1993). Accordingly, this
action was not subject to review under the Executive Order by the
Office of Information and Regulatory Affairs (OIRA) in the Office of
Management and Budget.
B. Review Under the Regulatory Flexibility Act
The Regulatory Flexibility Act (5 U.S.C. 601 et seq.) requires
preparation of an initial regulatory flexibility analysis (IFRA) for
any rule that by law must be proposed for public comment, unless the
agency certifies that the rule, if promulgated, will not have a
significant economic impact on a substantial number of small entities.
As required by Executive Order 13272, ``Proper Consideration of Small
Entities in Agency Rulemaking,'' 67 FR 53461 (August 16, 2002), DOE
published procedures and policies on February 19, 2003, to ensure that
the potential impacts of its rules on small entities are properly
considered during the DOE rulemaking process. 68 FR 7990. DOE has made
its procedures and policies available on the Office of the General
Counsel's Web site: http://energy.gov/gc/office-general-counsel.
DOE reviewed this proposed rule, which would amend the test
procedure for central air conditioners and heat pumps, under the
provisions of the Regulatory Flexibility Act and the procedures and
policies published on February 19, 2003. DOE tentatively concludes and
certifies that the proposed rule, if adopted, would not result in a
significant impact on a substantial number of small entities. The
factual basis for this certification is set forth below.
For the purpose of the regulatory flexibility analysis for this
rule, the DOE adopts the Small Business Administration (SBA) definition
of a small entity within this industry as a manufacturing enterprise
with 750 employees or fewer. DOE used the small business size standards
published on January 31, 1996, as amended, by the SBA to determine
whether any small entities would be required to comply with the rule.
61 FR 3280, 3286, as amended at 67 FR 3041, 3045 (Jan. 23, 2002) and at
69 FR 29192, 29203 (May 21, 2004); see also 65 FR 30836, 30850 (May 15,
2000), as amended at 65 FR 53533, 53545 (Sept. 5, 2000). The size
standards are codified at 13 CFR part 121. The standards are listed by
North American Industry Classification System (NAICS) code and industry
description and are available at www.sba.gov/idc/groups/public/documents/sba_homepage/serv_sstd_tablepdf.pdf.
Central air conditioner and heat pump manufacturing is classified
under NAICS 333415, ``Air-Conditioning and Warm Air Heating Equipment
and Commercial and Industrial Refrigeration Equipment Manufacturing.''
70 FR 12395 (March 11, 2005). DOE reviewed AHRI's listing of central
air conditioner and heat pump product manufacturer members and surveyed
the industry to develop a list of domestic manufacturers. As a result
of this review, DOE identified 22 manufacturers of central air
conditioners and heat pumps, of which 15 would be considered small
manufacturers with a total of approximately 3 percent of the market
sales. DOE seeks comment on its estimate of the number of small
entities that may be impacted by the proposed test procedure.
Potential impacts of the proposed test procedure on all
manufacturers, including small businesses, come from impacts associated
with the cost of proposed additional testing. In the June 2010 NOPR,
DOE estimated the incremental cost of the proposed additional tests
described in 10 CFR part 430, subpart B, Appendix M (proposed section
3.13) to be an increase of $1,000 to $1,500 per unit tested, indicating
that the largest additional cost would be associated with conducting
steady-state cooling mode tests and the dry climate tests for the SEER-
HD rating). 75 FR at 31243 (June 2, 2010). DOE has eliminated tests
associated with the SEER-HD rating from the proposals in this notice.
DOE conservatively estimates that off mode testing might cost $1,000
(roughly one-fifth of the $5000 cost of active mode testing--see 75 FR
at 31243 (June 2, 2010)). Assuming two off mode tests per tested model,
this is an average test cost of $2,000 per model.
The proposals of this notice also require that ICMs test one
combination of every basic model (i.e., model of indoor unit). Based on
a test cost estimate of $5000 and two tests per model, the costs for
this proposal are $10,000 for each basic model.
Because the incremental cost of running the extra off mode tests is
the same for all manufacturers, DOE believes that all manufacturers
would incur comparable costs for testing to certify off mode power use
for basic models as a result of the proposed test procedure. DOE
expects that small manufacturers will incur less testing expense
compared with larger manufacturers as a result of the proposed testing
requirements because they have fewer basic models and thus require
proportionally less testing when compared with large manufacturers that
have many basic models. DOE recognizes, however, that smaller
manufacturers may have less capital available over which to spread the
increased costs of testing.
With respect to the provisions addressing AEDMs, the proposals
contained herein would not increase the testing or reporting burden of
outdoor unit manufacturers who currently use, or are eligible to use,
an AEDM to certify their products. The proposal would eliminate the ARM
nomenclature and treat these methods as AEDMs, eliminate the pre-
approval requirement for product AEDMs, revise the requirements for
validation of an AEDM in a way that would not require more testing than
that required by the AEDM provisions included in the March 7, 2011
Certification, Compliance and Enforcement Final Rule (76 FR 12422)
(``March 2011 Final Rule''), and amend the process that DOE promulgated
in the March 2011 Final Rule for validating AEDMs and verifying
certifications based on the use of AEDMs. Because these AEDM-related
proposals would either have no effect on test burden or decrease burden
related to testing (e.g., elimination of ARM pre-approval), DOE has
determined these proposals would result in no significant change in
testing or reporting burden. The proposals contained herein would not
increase the testing or reporting burden of outdoor unit or independent
coil manufacturers besides the revision to the requirements for
validation of an AEDM, of which burden is outweighed by the benefit of
providing more accurate ratings for models of indoor units sold by
ICMs, as discussed in section III.A.3.d.
To evaluate the potential cost impact of the other test-related
proposals, DOE compared the cost of the testing to the total value
added by the manufacturers to determine whether the impact of the
proposed test procedure amendments is significant. The value added
represents the net economic value that a business creates when it takes
manufacturing inputs (e.g., materials) and turns them into
manufacturing outputs (e.g., manufactured goods). Specifically, as
defined by the U.S. Census, the value added statistic is calculated as
the total value of shipments (products
[[Page 69329]]
manufactured plus receipts for services rendered) minus the cost of
materials, supplies, containers, fuel, purchased electricity, and
contract work expenses.
DOE analyzed the impact on the smallest manufacturers of central
air conditioners and heat pumps because these manufacturers would
likely be the most vulnerable to cost increases. DOE calculated the
additional testing expense as a percentage of the average value added
statistic for the five individual firms in the 25 to 49 employee size
category in NAICS 333415 as reported by the U.S. Census (U.S. Bureau of
the Census, American Factfinder, 2002 Economic Census, Manufacturing,
Industry Series, Industry Statistics by Employment Size, http://factfinder.census.gov/servlet/EconSectorServlet?_lang=en&ds_name=EC0200A1&_SectorId=31&_ts=288639767147). The average annual value for manufacturers in this size range from
the census data was $1.26 million in 2001$, per the 2002 Economic
Census, or approximately $1.52 million per year in 2009$ after
adjusting for inflation using the implicit price deflator for gross
domestic product (U.S. Department of Commerce Bureau of Economic
Analysis, www.bea.gov/national/nipaweb/SelectTable.asp).
DOE also examined the average value added statistic provided by
census for all manufacturers with fewer than 500 employees in this
NAICS classification as the most representative value from the 2002
Economic Census data of the central air conditioner manufacturers with
fewer than 750 employees that are considered small businesses by the
SBA (15 manufacturers). The average annual value added statistic for
all small manufacturers with fewer than 500 employees was $7.88 million
(2009$).
Given this data, and assuming the range of estimates of additional
costs, $2,000 for OUMs and $10,000 for ICMs for the additional testing
costs, DOE concluded that the additional costs for testing of a single
basic model product under the proposed requirements would be up to
approximately 0.7 percent of annual value added for the 5 smallest
firms, and approximately 0.13 percent of the average annual value added
for all small central air conditioner or heat pump manufacturers (15
firms). DOE estimates that testing of basic models may not have to be
updated more than once every 5 years, and therefore the average
incremental burden of testing one basic model may be one fifth of these
values when the cost is spread over several years.
DOE requires that only the highest sales volume split-system
combinations be laboratory tested. 10 CFR 430.24(m). The majority of
central air conditioners and heat pumps offered by a manufacturer are
typically split-systems that are not required to be laboratory tested
but can be certified using an alternative rating method that does not
require DOE testing of these units. DOE reviewed the available data for
five of the smallest manufacturers to estimate the incremental testing
cost burden for those small firms that might experience the greatest
relative burden from the revised test procedure. These manufacturers
had an average of 10 models requiring testing (AHRI Directory of
Certified Product Performance, www.ahridirectory.org/ahridirectory/pages/home.aspx), while large manufacturers will have well over 100
such models. The additional testing cost for final certification for 10
models was estimated at $4,000 to $100,000. Meanwhile, these
certifications would be expected to last the product life, estimated to
be at least 5 years based on the time frame established in EPCA for DOE
review of central air conditioner efficiency standards. This test
burden is therefore estimated to be approximately 1.3 percent of the
estimated 5-year value added for the smallest five manufacturers. DOE
believes that these costs are not significant given other, much more
significant costs that the small manufacturers of central air
conditioners and heat pumps incur in the course of doing business. DOE
seeks comment on its estimate of the impact of the proposed test
procedure amendments on small entities and its conclusion that this
impact is not significant.
Accordingly, as stated above, DOE tentatively concludes and
certifies that this proposed rule would not have a significant economic
impact on a substantial number of small entities. Accordingly, DOE has
not prepared an initial regulatory flexibility analysis (IRFA) for this
rulemaking. DOE will provide its certification and supporting statement
of factual basis to the Chief Counsel for Advocacy of the SBA for
review under 5 U.S.C. 605(b).
C. Review Under the Paperwork Reduction Act of 1995
Manufacturers of central air conditioners and heat pumps must
certify to DOE that their products comply with any applicable energy
conservation standards. In certifying compliance, manufacturers must
test their products according to the DOE test procedures for central
air conditioners and heat pumps, including any amendments adopted for
those test procedures. DOE has established regulations for the
certification and recordkeeping requirements for all covered consumer
products and commercial equipment, including central air conditioners
and heat pumps. 76 FR 12422 (March 7, 2011); 80 FR 5099 (Jan. 30,
2015). The collection-of-information requirement for the certification
and recordkeeping is subject to review and approval by OMB under the
Paperwork Reduction Act (PRA). This requirement has been approved by
OMB under OMB control number 1910-1400. Public reporting burden for the
certification is estimated to average 20 hours per response, including
the time for reviewing instructions, searching existing data sources,
gathering and maintaining the data needed, and completing and reviewing
the collection of information.
Notwithstanding any other provision of the law, no person is
required to respond to, nor shall any person be subject to a penalty
for failure to comply with, a collection of information subject to the
requirements of the PRA, unless that collection of information displays
a currently valid OMB Control Number.
D. Review Under the National Environmental Policy Act of 1969
In this supplemental proposed rule, DOE proposes test procedure
amendments that it expects will be used to develop and implement future
energy conservation standards for central air conditioners and heat
pumps. DOE has determined that this rule falls into a class of actions
that are categorically excluded from review under the National
Environmental Policy Act of 1969 (42 U.S.C. 4321 et seq.) and DOE's
implementing regulations at 10 CFR part 1021. Specifically, this
proposed rule would amend the existing test procedures without
affecting the amount, quality or distribution of energy usage, and,
therefore, would not result in any environmental impacts. Thus, this
rulemaking is covered by Categorical Exclusion A5 under 10 CFR part
1021, subpart D, which applies to any rulemaking that interprets or
amends an existing rule without changing the environmental effect of
that rule. Accordingly, neither an environmental assessment nor an
environmental impact statement is required.
DOE's CX determination for this proposed rule is available at
http://energy.gov/nepa/categorical-exclusion-cx-determinations-cx
E. Review Under Executive Order 13132
Executive Order 13132, ``Federalism,'' 64 FR 43255 (August 4, 1999)
imposes certain requirements on agencies formulating and implementing
policies
[[Page 69330]]
or regulations that preempt State law or that have Federalism
implications. The Executive Order requires agencies to examine the
constitutional and statutory authority supporting any action that would
limit the policymaking discretion of the States and to carefully assess
the necessity for such actions. The Executive Order also requires
agencies to have an accountable process to ensure meaningful and timely
input by State and local officials in the development of regulatory
policies that have Federalism implications. On March 14, 2000, DOE
published a statement of policy describing the intergovernmental
consultation process it will follow in the development of such
regulations. 65 FR 13735. DOE has examined this proposed rule and has
determined that it would not have a substantial direct effect on the
States, on the relationship between the national government and the
States, or on the distribution of power and responsibilities among the
various levels of government. EPCA governs and prescribes Federal
preemption of State regulations as to energy conservation for the
products that are the subject of this proposed rule. States can
petition DOE for exemption from such preemption to the extent, and
based on criteria, set forth in EPCA. (42 U.S.C. 6297(d)) No further
action is required by Executive Order 13132.
F. Review Under Executive Order 12988
Regarding the review of existing regulations and the promulgation
of new regulations, section 3(a) of Executive Order 12988, ``Civil
Justice Reform,'' 61 FR 4729 (Feb. 7, 1996), imposes on Federal
agencies the general duty to adhere to the following requirements: (1)
Eliminate drafting errors and ambiguity; (2) write regulations to
minimize litigation; (3) provide a clear legal standard for affected
conduct rather than a general standard; and (4) promote simplification
and burden reduction. Section 3(b) of Executive Order 12988
specifically requires that Executive agencies make every reasonable
effort to ensure that the regulation: (1) Clearly specifies the
preemptive effect, if any; (2) clearly specifies any effect on existing
Federal law or regulation; (3) provides a clear legal standard for
affected conduct while promoting simplification and burden reduction;
(4) specifies the retroactive effect, if any; (5) adequately defines
key terms; and (6) addresses other important issues affecting clarity
and general draftsmanship under any guidelines issued by the Attorney
General. Section 3(c) of Executive Order 12988 requires Executive
agencies to review regulations in light of applicable standards in
sections 3(a) and 3(b) to determine whether they are met or it is
unreasonable to meet one or more of them. DOE has completed the
required review and determined that, to the extent permitted by law,
the proposed rule meets the relevant standards of Executive Order
12988.
G. Review Under the Unfunded Mandates Reform Act of 1995
Title II of the Unfunded Mandates Reform Act of 1995 (UMRA)
requires each Federal agency to assess the effects of Federal
regulatory actions on State, local, and Tribal governments and the
private sector. Pub. L. 104-4, sec. 201 (codified at 2 U.S.C. 1531).
For a proposed regulatory action likely to result in a rule that may
cause the expenditure by State, local, and Tribal governments, in the
aggregate, or by the private sector of $100 million or more in any one
year (adjusted annually for inflation), section 202 of UMRA requires a
Federal agency to publish a written statement that estimates the
resulting costs, benefits, and other effects on the national economy.
(2 U.S.C. 1532(a), (b)) The UMRA also requires a Federal agency to
develop an effective process to permit timely input by elected officers
of State, local, and Tribal governments on a proposed ``significant
intergovernmental mandate,'' and requires an agency plan for giving
notice and opportunity for timely input to potentially affected small
governments before establishing any requirements that might
significantly or uniquely affect small governments. On March 18, 1997,
DOE published a statement of policy on its process for
intergovernmental consultation under UMRA. 62 FR 12820; also available
at http://energy.gov/gc/office-general-counsel. DOE examined this
proposed rule according to UMRA and its statement of policy and
determined that the rule contains neither an intergovernmental mandate,
nor a mandate that may result in the expenditure of $100 million or
more in any year, so these requirements do not apply.
H. Review Under the Treasury and General Government Appropriations Act,
1999
Section 654 of the Treasury and General Government Appropriations
Act, 1999 (Pub. L. 105-277) requires Federal agencies to issue a Family
Policymaking Assessment for any rule that may affect family well-being.
This rule would not have any impact on the autonomy or integrity of the
family as an institution. Accordingly, DOE has concluded that it is not
necessary to prepare a Family Policymaking Assessment.
I. Review Under Executive Order 12630
DOE has determined, under Executive Order 12630, ``Governmental
Actions and Interference with Constitutionally Protected Property
Rights'' 53 FR 8859 (March 18, 1988), that this regulation would not
result in any takings that might require compensation under the Fifth
Amendment to the U.S. Constitution.
J. Review Under the Treasury and General Government Appropriations Act,
2001
Section 515 of the Treasury and General Government Appropriations
Act, 2001 (44 U.S.C. 3516 note) provides for agencies to review most
disseminations of information to the public under guidelines
established by each agency pursuant to general guidelines issued by
OMB. OMB's guidelines were published at 67 FR 8452 (Feb. 22, 2002), and
DOE's guidelines were published at 67 FR 62446 (Oct. 7, 2002). DOE has
reviewed this proposed rule under the OMB and DOE guidelines and has
concluded that it is consistent with applicable policies in those
guidelines.
K. Review Under Executive Order 13211
Executive Order 13211, ``Actions Concerning Regulations That
Significantly Affect Energy Supply, Distribution, or Use,'' 66 FR 28355
(May 22, 2001), requires Federal agencies to prepare and submit to OMB,
a Statement of Energy Effects for any proposed significant energy
action. A ``significant energy action'' is defined as any action by an
agency that promulgated or is expected to lead to promulgation of a
final rule, and that: (1) Is a significant regulatory action under
Executive Order 12866, or any successor order; and (2) is likely to
have a significant adverse effect on the supply, distribution, or use
of energy; or (3) is designated by the Administrator of OIRA as a
significant energy action. For any proposed significant energy action,
the agency must give a detailed statement of any adverse effects on
energy supply, distribution, or use should the proposal be implemented,
and of reasonable alternatives to the action and their expected
benefits on energy supply, distribution, and use.
The proposed regulatory action to amend the test procedure for
measuring the energy efficiency of central air conditioners and heat
pumps is not a significant regulatory action under Executive Order
12866. Moreover, it
[[Page 69331]]
would not have a significant adverse effect on the supply,
distribution, or use of energy, nor has it been designated as a
significant energy action by the Administrator of OIRA. Therefore, it
is not a significant energy action, and, accordingly, DOE has not
prepared a Statement of Energy Effects.
L. Review Under Section 32 of the Federal Energy Administration Act of
1974
Under section 301 of the Department of Energy Organization Act
(Pub. L. 95-91; 42 U.S.C. 7101), DOE must comply with section 32 of the
Federal Energy Administration Act of 1974, as amended by the Federal
Energy Administration Authorization Act of 1977. (15 U.S.C. 788; FEAA)
Section 32 essentially provides in relevant part that, where a proposed
rule authorizes or requires use of commercial standards, the notice of
proposed rulemaking must inform the public of the use and background of
such standards. In addition, section 32(c) requires DOE to consult with
the Attorney General and the Chairman of the Federal Trade Commission
(FTC) concerning the impact of the commercial or industry standards on
competition.
The proposed rule incorporates testing methods contained in the
following commercial standards: AHRI 210/240-2008 with Addendum 1 and
2, Performance Rating of Unitary Air-Conditioning & Air-Source Heat
Pump Equipment; and ANSI/AHRI 1230-2010 with Addendum 2, Performance
Rating of Variable Refrigerant Flow Multi-Split Air-Conditioning and
Heat Pump Equipment. While the proposed test procedure is not
exclusively based on AHRI 210/240-2008 or ANSI/AHRI 1230-2010, one
component of the test procedure, namely test setup requirements, adopts
language from AHRI 210/240-2008 without amendment; and another
component of the test procedure, namely test setup and test performance
requirements for multi-split-systems, adopts language from ANSI/AHRI
1230-2010 without amendment. The Department has evaluated these
standards and is unable to conclude whether they fully comply with the
requirements of section 32(b) of the FEAA, (i.e., that they were
developed in a manner that fully provides for public participation,
comment, and review). DOE will consult with the Attorney General and
the Chairman of the FTC concerning the impact of these test procedures
on competition, prior to prescribing a final rule.
M. Description of Materials Incorporated by Reference
In this SNOPR, DOE proposes to incorporate by reference (IBR) the
following two test standards published by AHRI: ANSI/AHRI 210/240-2008
with Addenda 1 and 2, titled ``Performance Rating of Unitary Air-
Conditioning & Air-Source Heat Pump Equipment;'' and ANSI/AHRI 1230-
2010 with Addendum 2, titled ``Performance Rating of Variable
Refrigerant Flow (VRF) Multi-Split Air-Conditioning and Heat Pump
Equipment.'' DOE also proposes to IBR a draft version of ASHRAE 210/240
which has not yet been published. DOE also proposes to update its IBR
to the most recent version of the following standards published by
ASHRAE: ASHRAE 23.1-2010 titled ``Methods of Testing for Rating the
Performance of Positive Displacement Refrigerant Compressors and
Condensing Units that Operate at Subcritical Temperatures of the
Refrigerant'', ASHRAE Standard 37-2009, Methods of Testing for Rating
Electrically Driven Unitary Air-Conditioning and Heat Pump Equipment,
ASHRAE 41.1-2013 titled ``Standard Method for Temperature
Measurement'', ASHRAE 41.6-2014 titled ``Standard Method for Humidity
Measurement'', and ASHRAE 41.9-2011titled ``Standard Methods for
Volatile-Refrigerant Mass Flow Measurements Using Calorimeters''.
Finally, DOE proposes to updates its IBR to the most recent version of
the following test procedure from ASHRAE and AMCA: ASHRAE/AMCA 51-07/
210-07, Laboratory Methods of Testing Fans for Certified Aerodynamic
Performance Rating.
ANSI/AHRI 210/240-2008 is an industry accepted test procedure that
measures the cooling and heating performance of central air
conditioners and heat pumps and is applicable to products sold in North
America. The test procedure proposed in this SNOPR references various
sections of ANSI/AHRI 210/240-2008 that address test setup, test
conditions, and rating requirements. ANSI/AHRI 210/240-2008 is readily
available on AHRI's Web site at http://www.ahrinet.org/site/686/Standards/HVACR-Industry-Standards/Search-Standards. AHRI Standard 210/
240-Draft is a draft version of AHRI 210/240 that AHRI provided to DOE
in 2015. AHRI Standard 210/240-Draft will supersede the 2008 version
once it is published. The draft version is available on the rulemaking
Web page (Docket EERE-2009-BT-TP-0004-0045).
ANSI/AHRI 1230-2010 is an industry accepted test procedure that
measures the cooling and heating performance of variable refrigerant
flow (VRF) multi-split air conditioners and heat pumps and is
applicable to products sold in North America. The test procedure
proposed in this SNOPR for VRF multi-split systems references various
sections of ANSI/AHRI 1230-2010 that address test setup, test
conditions, and rating requirements. ANSI/AHRI 1230-2010 is readily
available on AHRI's Web site at http://www.ahrinet.org/site/686/Standards/HVACR-Industry-Standards/Search-Standards.
ASHRAE 23.1-2010 is an industry accepted test procedure for rating
the thermodynamic performance of positive displacement refrigerant
compressors and condensing units that operate at subcritical
temperatures. The test procedure proposed in this SNOPR references
sections of ASHRAE 23.1-2010 that address requirements, instruments,
methods of testing, and testing procedure specific to compressor
calibration. ASHRAE 23.1-2010 can be purchased from ASHRAE's Web site
at https://www.ashrae.org/resources-publications.
ASHRAE Standard 37-2009 is an industry accepted standard that
provides test methods for determining the cooling capacity of unitary
air-conditioning equipment and the cooling or heating capacities, or
both, of unitary heat pump equipment. The test procedure proposed in
this SNOPR references various sections of ASHRAE Standard 37-2009 that
address test conditions and test procedures. The current DOE test
procedure references a previous version of this standard, ASHRAE 37-
2005. ASHRAE Standard 37-2009 can be purchased from ASHRAE's Web site
at https://www.ashrae.org/resources-publications.
ASHRAE 41.1-2013 is an industry accepted method for measuring
temperature in testing heating, refrigerating, and air-conditioning
equipment. The test procedure proposed in this SNOPR references
sections of ASHRAE 41.1-2013 that address requirements, instruments,
and methods for measuring temperature. ASHRAE 41.1-2013 can be
purchased from ASHRAE's Web site at https://www.ashrae.org/resources-publications.
ASHRAE 41.6-2014 is an industry accepted test method for measuring
humidity of moist air. The test procedure proposed in this SNOPR
references sections of ASHRAE 41.6-2014 that address requirements,
instruments, and methods for measuring humidity. ASHRAE 41.6-2014 can
be purchased from ASHRAE's Web site at https://www.ashrae.org/resources-publications.
[[Page 69332]]
ASHRAE 41.9-2011 is an industry accepted standard that provides
recommended practices for measuring the mass flow rate of volatile
refrigerants using calorimeters. The test procedure proposed in this
SNOPR references sections of ASHRAE 41.9-2011 that address
requirements, instruments, and methods for measuring refrigerant flow
during compressor calibration. ASHRAE 41.9-2011 can be purchased from
ASHRAE's Web site at https://www.ashrae.org/resources-publications.
ASHRAE/AMCA 51-07/210-07 is an industry accepted standard that
establishes uniform test methods for a laboratory test of a fan or
other air moving device to determine its aerodynamic performance in
terms of air flow rate, pressure developed, power consumption, air
density, speed of rotation, and efficiency for rating or guarantee
purposes. The test procedure in this SNOPR references various sections
of ASHRAE/AMCA 51-07/210-07 that address test conditions. The current
DOE test procedure references a previous version of this standard,
ASHRAE/AMCA 51-99/210-99. ASHRAE/AMCA 51-07/210-07 can be purchased
from AMCA's Web site at http://www.amca.org/store/index.php.
V. Public Participation
A. Submission of Comments
DOE will accept comments, data, and information regarding this
proposed rule no later than the date provided in the DATES section at
the beginning of this proposed rule. Interested parties may submit
comments using any of the methods described in the ADDRESSES section at
the beginning of this notice.
Submitting comments via regulations.gov. The regulations.gov Web
page will require you to provide your name and contact information.
Your contact information will be viewable to DOE Building Technologies
staff only. Your contact information will not be publicly viewable
except for your first and last names, organization name (if any), and
submitter representative name (if any). If your comment is not
processed properly because of technical difficulties, DOE will use this
information to contact you. If DOE cannot read your comment due to
technical difficulties and cannot contact you for clarification, DOE
may not be able to consider your comment.
However, your contact information will be publicly viewable if you
include it in the comment or in any documents attached to your comment.
Any information that you do not want to be publicly viewable should not
be included in your comment, nor in any document attached to your
comment. Persons viewing comments will see only first and last names,
organization names, correspondence containing comments, and any
documents submitted with the comments.
Do not submit to regulations.gov information for which disclosure
is restricted by statute, such as trade secrets and commercial or
financial information (hereinafter referred to as Confidential Business
Information (CBI)). Comments submitted through regulations.gov cannot
be claimed as CBI. Comments received through the Web site will waive
any CBI claims for the information submitted. For information on
submitting CBI, see the Confidential Business Information section.
DOE processes submissions made through regulations.gov before
posting. Normally, comments will be posted within a few days of being
submitted. However, if large volumes of comments are being processed
simultaneously, your comment may not be viewable for up to several
weeks. Please keep the comment tracking number that regulations.gov
provides after you have successfully uploaded your comment.
Submitting comments via email, hand delivery, or mail. Comments and
documents submitted via email, hand delivery, or mail also will be
posted to regulations.gov. If you do not want your personal contact
information to be publicly viewable, do not include it in your comment
or any accompanying documents. Instead, provide your contact
information on a cover letter. Include your first and last names, email
address, telephone number, and optional mailing address. The cover
letter will not be publicly viewable as long as it does not include any
comments.
Include contact information each time you submit comments, data,
documents, and other information to DOE. If you submit via mail or hand
delivery, please provide all items on a CD, if feasible. It is not
necessary to submit printed copies. No facsimiles (faxes) will be
accepted.
Comments, data, and other information submitted to DOE
electronically should be provided in PDF (preferred), Microsoft Word or
Excel, WordPerfect, or text (ASCII) file format. Provide documents that
are not secured, written in English and free of any defects or viruses.
Documents should not contain special characters or any form of
encryption and, if possible, they should carry the electronic signature
of the author.
Campaign form letters. Please submit campaign form letters by the
originating organization in batches of between 50 to 500 form letters
per PDF or as one form letter with a list of supporters' names compiled
into one or more PDFs. This reduces comment processing and posting
time.
Confidential Business Information. According to 10 CFR 1004.11, any
person submitting information that he or she believes to be
confidential and exempt by law from public disclosure should submit via
email, postal mail, or hand delivery two well-marked copies: One copy
of the document marked confidential including all the information
believed to be confidential, and one copy of the document marked non-
confidential with the information believed to be confidential deleted.
Submit these documents via email or on a CD, if feasible. DOE will make
its own determination about the confidential status of the information
and treat it according to its determination.
Factors of interest to DOE when evaluating requests to treat
submitted information as confidential include: (1) A description of the
items; (2) whether and why such items are customarily treated as
confidential within the industry; (3) whether the information is
generally known by or available from other sources; (4) whether the
information has previously been made available to others without
obligation concerning its confidentiality; (5) an explanation of the
competitive injury to the submitting person which would result from
public disclosure; (6) when such information might lose its
confidential character due to the passage of time; and (7) why
disclosure of the information would be contrary to the public interest.
It is DOE's policy that all comments may be included in the public
docket, without change and as received, including any personal
information provided in the comments (except information deemed to be
exempt from public disclosure).
B. Issues on Which DOE Seeks Comment
Although DOE welcomes comments on any aspect of this proposal, DOE
is particularly interested in receiving comments and views of
interested parties concerning the following issues:
1. The details characterizing the same model of indoor unit, same
model of outdoor unit, and same single-package model;
2. Its proposed changes to the determination of certified ratings
for single-split-system air conditioners, specifically in its proposed
phased approach where in the first phase
[[Page 69333]]
manufacturers must certify all models of outdoor units with the model
of coil-only indoor unit that is likely to have the largest volume of
retail sales with the particular model of outdoor unit but may use the
model of blower coil indoor unit likely to have the highest sales if
the model of outdoor unit is sold only with models of blower coil
indoor units, and may use testing or AEDMs to rate other combinations;
and in the second phase manufacturers must certify all models of
outdoor units with the model of blower coil indoor unit that is likely
to have the largest volume of retail sales with that model of outdoor
unit but must rate other blower coil or coil-only combinations through
testing or AEDMs;
3. Its proposed definitions for blower coil and coil-only indoor
units;
4. Whether additional testing and rating requirements are necessary
for multi-split systems paired with models of conventional ducted
indoor units rather than short-duct units;
5. Whether manufacturers or other stakeholders support ratings for
mix-match multi-split systems including models of both SDHV and non-
ducted or short-ducted indoor units, and if so, how they should be
rated (i.e., by by taking the mean of a sample of tested non-ducted
units and a sample of tested SDHV units or by testing a combination on
non-ducted and SDHV units), and whether the SDHV or split-system
standard would be most appropriate;
6. Whether manufacturers support having the ability to test mix-
match systems using the test procedure rather than rating them using an
average of the other tested systems;
7. Whether manufacturers support the rating of mix-match systems
using other than a straight mean, such as a weighting by the number of
non-ducted or short-ducted units;
8. Whether the definition of ``tested combination'' is appropriate
for rating specific individual combinations, or whether manufacturers
want more flexibility such as testing with more than 5 indoor units;
9. Information and data on manufacturing and testing variability
associated with multi-split systems that would allow it to understand
how a single unit may be representative of the population and what
tolerances would need to be applied to ratings based on a single unit
sample in order to account for variability;
10. The basic model definition in section III.A.1;
11. Its proposal for ICMs to test each model of indoor unit with
the lowest-SEER model of outdoor unit that is certified as a part of a
basic model by an OUM as well as any test burden associated with this
proposal;
12. The likelihood of multiple individual models of single-package
units meeting the requirements proposed in the basic model definition
to be assigned to the same basic model;
13. Whether, if manufacturers are able to assign multiple
individual single-package models to a single basic model, whether
manufacturers would want to use an AEDM to rate other individual models
within the same basic model other than the lowest SEER individual
model;
14. Whether manufacturers would want to employ an AEDM to rate the
off-mode power consumption for other variations of off-mode associated
with the single-package basic model other than the variation tested;
15. The reporting burden associated with the proposed certification
reporting requirements proposed in this notice;
16. The additions to the represented value requirements for cooling
capacity, heating capacity, and SHR, as well as the proposed rounding
requirements;
17. The proposal to not require additional testing to validate an
AEDM beyond the testing required under 429.16(a)(2)(ii) for split-
system air conditioners and heat pumps where manufacturers must test
each basic model, being each model of outdoor unit, with at least one
model of indoor unit;
18. The proposal that ICMs must use the combinations they would be
required to test, under 429.16, to validate an AEDM that is intended to
be used for other individual combinations within each basic model;
19. Whether the approach to not penalize manufacturers for applying
conservative ratings to their products is reasonable to identify an
individual combination's failure to meet its certified rating;
20. Whether manufacturers would typically apply more than one AEDM,
and if they would, the differences between such AEDMs;
21. Its proposal for multi-circuit products to adopt the same
common duct testing approach used for testing multi-split products; and
whether this method will yield accurate results that are representative
of the true performance of these systems;
22. Its proposals for multi-blower products, including whether
individual adjustments of each blower are appropriate and whether
external static pressures measured for individual tests may be
different;
23. Its proposal to require a test for off mode power consumption
at 722 [deg]F, a second test at the temperature below a
turn-on temperature specified by the manufacturer, a tolerance on the
temperature, and the proposal that manufacturers include in
certification reports the temperatures at which the crankcase heater is
designed to turn on and turn off for the heating season, if applicable;
24. The proposal to replace the off mode test at 57 [deg]F with a
test at a temperature which is 52 [deg]F below a
manufacturer-specified turn-on temperature to maintain the intent of
the off mode power consumption rating as a rating that measures the off
mode power consumption for the heating season, and allay the
stakeholders' concerns of a loophole at the 57 [deg]F test point;
25. The proposal to use a per-compressor off mode power consumption
metric so as to not penalize manufacturers of products with multiple
compressor systems, which are highly efficient and require larger
crankcase heaters for safe and reliable operation;
26. The proposal on the multiplier of 1.5 for determining the
shoulder season and heating season per-compressor off mode power so as
to not penalize manufacturers of products with modulated compressors,
which require a larger crankcase heater to ensure safe and reliable
operation;
27. The proposal to more accurately reflect the off mode power
consumption for coil-only and blower coil split-system units by
excluding the low-voltage power from the indoor unit when measuring off
mode power consumption for coil-only split-system air conditioners and
including the low-voltage power from the indoor unit when measuring off
mode power consumption for blower coil split-system air conditioning
and heat pumps;
28. The proposal to incent manufacturers of products with time
delays by adopting a credit to shoulder season energy consumption that
is proportional to the duration of the delay or a default of 25%
savings in shoulder season off mode energy consumption and the
possibility of a verification test for length of time delay;
29. The proposal to add optional informational equations to
determine the actual off mode energy consumption, based on the hours of
off mode operation and off mode power for the shoulder and heating
seasons;
30. Whether regulating crankcase heater energy consumption has a
negative impact on product reliability in light of the test method
proposed in this rule;
[[Page 69334]]
31. The proposal to improve repeatability of testing central air
conditioner and heat pump products by requiring the lowest fan speed
setting that meets minimum static pressure and maximum air volume rate
requirements for blower coil systems and requiring the lowest fan speed
settings that meets the maximum static pressure and maximum air volume
rate requirements for coil-only indoor units;
32. The proposal to mirror how insulation is installed in the field
by requiring test laboratories either install the insulation shipped
with the unit or use insulation as specified in the manufacturer's
installation manuals included with the unit;
33. The proposal to clarify liquid refrigerant line insulation
requirements by requiring such insulation only if the product is a
heating-only heat pump;
34. The proposal to prevent thermal losses from the refrigerant
mass flow meter to the floor by requiring a thermal barrier if the
meter is not mounted on a pedestal or is not elevated;
35. The proposal to require either an air sampling device used on
all outdoor unit air-inlet surfaces or demonstration of air temperature
uniformity for the outdoor unit vis-a-vis 1.5 [deg]F maximum spread of
temperatures measured by thermocouples distributed one thermocouple per
square feet of air-inlet surface of the outdoor unit;
36. The proposal to require that the dry bulb temperature and
humidity measurements used to verify that the required outdoor air
conditions have been maintained be measured for the air collected by
the air sampling device (e.g., rather than being measured by
temperature sensors located in the air stream approaching the air
inlets);
37. The proposal to limit thermal losses by preventing the air
sampling device from nearing the test chamber floor, insulating air
sampling device surfaces, and requiring dry bulb and humidity
measurements be made at the same location in the air sampling device;
38. The proposal to fix maximum compressor speed when testing at
each of the outdoor temperature for those control systems that vary
maximum compressor speed with outdoor temperature;
39. The proposal to prevent improper refrigerant charging
techniques by requiring charging of near-azeotropic and zeotropic
refrigerant blends in the liquid state only;
40. The proposal to require, for air conditioners and cooling-and-
heating heat pumps refrigerant charging at the A or A2 test
condition, and for heating-only heat pumps refrigerant charging at the
H1 or H12 test condition, to meet a 12 2 [deg]F superheat temperature requirement for units equipped
with fixed orifice type metering devices and a 10 2 [deg]F
subcooling temperature requirement for units equipped with thermostatic
expansion valve or electronic expansion valve type metering devices, if
no manufacturer installation instructions provide guidance on charging
procedures;
41. The proposal to verify functionality of heat pumps at the
H1 or H12 test condition after charging at the A
or A2 test condition, and if non-functional, the proposal to
adjust refrigerant charge to the requirements of the proposed
standardized charging procedure at the H1 or H12
test condition;
42. The proposal to require refrigerant charging based on the
outdoor installation instructions for outdoor unit manufacturer
products and refrigerant charging based on the indoor installation
instructions for independent coil manufacturer products, where both the
indoor and outdoor installation instructions are provided and advise
differently, unless otherwise specified by either installation
instructions;
43. The proposal to require installation of pressure gauges and
verification of refrigerant charge amount and, if charging instructions
are not available adjust charge based on the proposed refrigerant
charging procedure;
44. All aspects of its proposals to amend the refrigerant charging
procedures;
45. The proposal to allow for cyclic tests of single-package ducted
units an upturned duct as an alternative arrangement to replace the
currently-required damper in the inlet portion of the indoor air
ductwork;
46. The proposal to further justify adequacy of the alternative
arrangement in preventing thermal losses during the OFF portion of the
cyclic test by proposing installing a dry bulb temperature sensor near
the indoor inlet and requiring the maximum permissible range of the
recorded temperatures during the OFF period be no greater than 1.0
[deg]F;
47. The proposed revisions to the cyclic test procedure for the
determination of both the cooling and heating coefficient of
degradation, including additional test data that would support the
proposed specifications, or changes to, the number of warm-up cycles,
the cycle time for variable speed units, the number of cycles averaged
to obtain the value, and the stability criteria;
48. The proposal to allay stakeholder concerns regarding compressor
break-in period by allowing an optional break-in period of up to 20
hours prior to testing;
49. Its proposed limitation of incorporation by reference to
industry standards to specific sections necessary for the test
procedure, including any specific sections stakeholders feel should be
referenced that are not;
50. The proposed sampling interval for dry-bulb temperatures, wet
bulb temperature, dew point temperature, and relative humidity;
51. The appropriate use of the target value and maximum tolerances
for refrigerant charging, as well as data to support the appropriate
selection of tolerance;
52. The proposal for damping pressure transducer signals including
whether the proposed maximum time constant is appropriate;
53. Setting a definition for short duct systems to mean ducted
systems whose indoor units can deliver no more than 0.07 in. wc. ESP
when delivering the full load air volume rate for cooling operation,
and requiring such systems meet the minimum ESP levels as proposed in
the NOPR: 0.03 in. wc. for units less than 28,800 Btu/h; 0.05 in. wc.
for units between 29,000 Btu/h and 42,500 Btu/h; and 0.07 in. wc. for
units greater than 43,000 Btu/h;
54. The incorporation by reference of AHRI 1230-2010, and in
particular the specific sections of Appendix M and AHRI 1230-2010 that
DOE proposes to apply to testing VRF systems;
55. The proposed change to the informative tables at the beginning
of Section 2. Testing Conditions and/or whether additional
modifications to the new table could be implemented to further improve
clarity;
56. Its proposal to delete the definition of mini-split air
conditioners and heat pumps, and define (1) single-zone-multiple-coil
split-system to represent a split-system that has one outdoor unit and
that has two or more coil-only or blower coil indoor units connected
with a single refrigeration circuit, where the indoor units operate in
unison in response to a single indoor thermostat; and (2) single-split-
system to represent a split-system that has one outdoor unit and that
has one coil-only or blower coil indoor unit connected to its other
component(s) with a single refrigeration circuit;
57. Its proposal to include in the ESP requirement a pressure drop
contribution associated with average typical filter and indoor coil
fouling levels and its use of residential-based indoor coil and filter
fouling pressure drop data to estimate the appropriate
[[Page 69335]]
ESP contribution; DOE also requests data that would validate the
proposed ESP contributions or suggest adjustments that should be made
to improve representativeness of the values in this proposal;
58. Its proposals to set higher minimum ESP requirements for
systems other than multi-split systems and small-duct, high-velocity
systems and report the external static pressure used during their
certification tests;
59. Its proposal to implement an allowance in ESP for air-
conditioning units tested in blower-coil (or single-package)
configuration in which a condensing furnace is in the air flow path
during the test. DOE seeks comment regarding the proposed 0.1 in. wc.
ESP reduction for such tests, including test data to support
suggestions regarding different reductions.
60. Its proposal to revise the heating load line that shifts the
heating balance point and zero load point to lower ambient temperatures
that better reflect field operations and energy use characteristics, as
well as its proposal to perform cyclic testing for variable speed heat
pumps at 47 [deg]F instead of at 62 [deg]F;
61. Whether, in the case that the proposed heating load line is not
adopted, DOE should modify the HSPF rating procedure for variable speed
heat pumps at mid-range outdoor temperatures using option 1: Which
entails basing performance on minimum speed tests at 47 [deg]F and
intermediate speed test at 35 [deg]F and is the less accurate option
but has no additional test burden; or option 2: Which entails basing
performance on minimum speed tests at 47 [deg]F and at 35 [deg]F and is
more accurate but with higher test burden;
62. Test results and other data regarding whether HSPF results for
other variable speed heat pumps would be more significantly impacted by
this change to the test procedure to test at maximum speed at 2 [deg]F
outdoor temperature or at low cutoff temperature, whichever is higher
(in conjunction with the test at maximum speed at 17 [deg]F outdoor
temperature) as well as whether the additional test burden would offset
the advantages of the proposed modification;
63. The estimate of the number of small entities that may be
impacted by the proposed test procedure and its conclusion that the
impact is not significant.
VI. Approval of the Office of the Secretary
The Secretary of Energy has approved publication of this proposed
rule.
List of Subjects
10 CFR Part 429
Administrative practice and procedure, Confidential business
information, Energy conservation, Reporting and recordkeeping
requirements.
10 CFR Part 430
Administrative practice and procedure, Confidential business
information, Energy conservation, Energy conservation test procedures,
Household appliances, Imports, Incorporation by reference,
Intergovernmental relations, Small businesses.
Issued in Washington, DC, on August 21, 2015.
Kathleen B. Hogan,
Deputy Assistant Secretary for Energy Efficiency, Energy Efficiency and
Renewable Energy.
For the reasons set forth in the preamble, DOE proposes to amend
parts 429 and 430 of chapter II of Title 10, Subpart B, Code of Federal
Regulations, to read as follows:
PART 429--CERTIFICATION, COMPLIANCE, AND ENFORCEMENT FOR CONSUMER
PRODUCTS AND COMMERCIAL AND INDUSTRIAL EQUIPMENT
0
1. The authority citation for part 429 continues to read as follows:
Authority: 42 U.S.C. 6291-6317.
0
2. Amend Sec. 429.12 by revising paragraphs (b)(8) and (12) to read as
follows:
Sec. 429.12 General requirements applicable to certification reports.
* * * * *
(b) * * *
(8) The test sample size (i.e., number of units tested for the
basic model, or in the case of single- split-system central air
conditioners and central air conditioning heat pumps, for each
individual combination). Enter ``0'' if an AEDM was used in lieu of
testing;
* * * * *
(12) If the test sample size is listed as ``0'' to indicate the
certification is based upon the use of an alternate way of determining
measures of energy conservation, identify the method used for
determining measures of energy conservation (such as ``AEDM,'' or
linear interpolation). Manufacturers of commercial packaged boilers,
commercial water heating equipment, commercial refrigeration equipment,
and commercial HVAC equipment must provide the manufacturer's
designation (name or other identifier) of the AEDM used; and
* * * * *
0
3. Section 429.16 is revised to read as follows:
Sec. 429.16 Central air conditioners and central air conditioning
heat pumps.
(a) Determination of Certified Rating. Determine the certified
rating for each basic model through testing pursuant to paragraph
(a)(1)(ii) of this section. For single-split-systems, manufacturers
must certify additional ratings for each individual combination within
the same basic model either based on testing or by using an AEDM
subject to the limitations of paragraph (a)(2) of this section. This
includes blower coil and coil-only systems both before and after the
compliance date of any amended energy conservation standards. For
multi-split, multi-circuit, and single-zone-multiple-coil systems, each
basic model must include a rating for a non-ducted combination and may
also include ratings for a ducted combination and a mixed non-ducted/
short-ducted combination per the requirements specified in this
section. If individual models of single-package systems or individual
combinations of split-systems that are otherwise identical are offered
with multiple options for off mode-related components, rate the
individual model/combination with the crankcase heater and controls
that are the most consumptive. A manufacturer may also certify less
consumptive off mode options; however, the manufacturer must
differentiate the individual model numbers in its certification report.
(1) Units to be tested.
(i) General. The general requirements of Sec. 429.11 apply to
central air conditioners and heat pumps; and
(ii) Model selection for testing. (A) Except for single-split-
system non-space-constrained air conditioners, determine represented
values for each basic model through testing of the following, specific,
individual model or combination pursuant to the table below.
----------------------------------------------------------------------------------------------------------------
Category Equipment type Must test each: With:
----------------------------------------------------------------------------------------------------------------
Single-Package Unit................ Single-Package AC..... Basic Model........... Lowest SEER individual
model.
[[Page 69336]]
Single-Package HP.....
Space-Constrained
Single-Package AC.
Space-Constrained
Single-Package HP.
Outdoor Unit and Indoor Unit (Rated Single-Split-System HP Model of Outdoor Unit. The model of indoor unit
by OUM). that is likely to have the
largest volume of retail
sales with the particular
model of outdoor unit.
Space-Constrained
Split-System AC.
Space-Constrained
Split-System HP.
Multi-Split, Multi- Model of Outdoor Unit. At a minimum, a ``tested
Circuit, or Single- combination'' composed
Zone-Multiple-Coil entirely of non-ducted
Split System. indoor units. For any
models of outdoor units
also sold with models of
short-ducted indoor units,
a second ``tested
combination'' composed
entirely of short-ducted
indoor units must be
tested (in addition to the
non-ducted combination).
For any models of outdoor
units also sold with
models of SDHV indoor
units, a second (or third)
``tested combination''
composed entirely of SDHV
units must be tested (in
addition to the non-ducted
combination and, if
tested, the short-ducted
combination).
Indoor Unit Only (Rated by ICM).... Single-Split-System... Model of Indoor Unit.. Least efficient model of
outdoor unit with which it
will be paired, where the
least efficient model of
outdoor unit is the
outdoor unit in the lowest
SEER combination as
certified by the OUM). If
there are multiple models
of outdoor units with the
same lowest-SEER rating,
the ICM may select one for
testing purposes.
Small-Duct, High
Velocity Systems.
Outdoor Unit Only.................. Outdoor Unit Only..... Model of Outdoor Unit. Model of indoor unit
meeting the requirements
of section 2.2e of
Appendix M (or M1) to
Subpart B of 10 CFR Part
430.
----------------------------------------------------------------------------------------------------------------
(B) For single-split-system, non-space-constrained air conditioners
rated by OUMs, determine represented values for each basic model
through testing of the following, specific, individual combination,
with requirements depending on date and pursuant to the table below.
----------------------------------------------------------------------------------------------------------------
Date Equipment type Must test each: With:
----------------------------------------------------------------------------------------------------------------
Before the compliance date of any Split-System AC with Model of Outdoor Unit. The model of coil-only
amended energy conservation single capacity indoor unit that is likely
standards (with a compliance date condensing unit. to have the largest volume
after January 1, 2017). of retail sales with the
particular model of
outdoor unit.
Split-System AC with Model of Outdoor Unit. The model of coil-only
other than single indoor unit that is likely
capacity condensing to have the largest volume
unit. of retail sales with the
particular model of
outdoor unit, unless the
model of outdoor unit is
only sold with model(s) of
blower coil indoor units,
in which case the model of
blower coil indoor unit
(with designated air mover
as applicable) that is
likely to have the largest
volume of retail sales
with the particular model
of outdoor unit.
On or after the compliance date of Split-system AC....... Model of Outdoor Unit. The model of blower coil
any amended energy conservation indoor unit that is likely
standards with which compliance is to have the largest volume
required on or after January 1, of retail sales with the
2017. particular model of
outdoor unit.
----------------------------------------------------------------------------------------------------------------
(iii) Sampling plans and representative values. (A) Each basic
model (for single-package systems) or individual combination (for
split-systems) tested must have a sample of sufficient size tested in
accordance with the applicable provisions of this subpart. The
represented values for any basic model or individual combination must
be assigned such that:
(1) Any represented value of power consumption or other measure of
energy consumption for which consumers would favor lower values must be
greater than or equal to the higher of:
(i) The mean of the sample, where:
[GRAPHIC] [TIFF OMITTED] TP09NO15.003
and x is the sample mean; n is the number of samples; and
xi is the ith sample; Or,
[[Page 69337]]
(ii) The upper 90 percent confidence limit (UCL) of the true mean
divided by 1.05, where:
[GRAPHIC] [TIFF OMITTED] TP09NO15.004
And x is the sample mean; s is the sample standard deviation; n is
the number of samples; and t0.90 is the t statistic for a
90% one-tailed confidence interval with n-1 degrees of freedom (from
Appendix D).
(2) Any represented value of the energy efficiency or other measure
of energy consumption for which consumers would favor higher values
shall be less than or equal to the lower of:
(i) The mean of the sample, where:
[GRAPHIC] [TIFF OMITTED] TP09NO15.005
and, x is the sample mean; n is the number of samples; and
xi is the ith sample; or,
(ii) The lower 90 percent confidence limit (LCL) of the true mean
divided by 0.95, where:
[GRAPHIC] [TIFF OMITTED] TP09NO15.006
And x is the sample mean; s is the sample standard deviation; n is
the number of samples; and t0.90 is the t statistic for a
90% one-tailed confidence interval with n-1 degrees of freedom (from
Appendix D).
(3) The represented value of cooling capacity is the mean of the
capacities measured for the sample, rounded:
(i) To the nearest 100 Btu/h if cooling capacity is less than
20,000 Btu/h,
(ii) To the nearest 200 Btu/h if cooling capacity is greater than
or equal to 20,000 Btu/h but less than 38,000 Btu/h, and
(iii) To the nearest 500 Btu/h if cooling capacity is greater than
or equal to 38,000 Btu/h and less than 65,000 Btu/h.
(4) The represented value of heating capacity is the mean of the
capacities measured for the sample, rounded:
(i) To the nearest 100 Btu/h if heating capacity is less than
20,000 Btu/h,
(ii) To the nearest 200 Btu/h if heating capacity is greater than
or equal to 20,000 Btu/h but less than 38,000 Btu/h, and
(iii) To the nearest 500 Btu/h if heating capacity is greater than
or equal to 38,000 Btu/h and less than 65,000 Btu/h.
(5) The represented value of sensible heat ratio (SHR) is the mean
of the SHR measured for the sample, rounded to the nearest percent (%).
(B) For heat pumps (other than heating-only heat pumps), all units
of the sample population must be tested in both the cooling and heating
modes and the results used for determining all representations.
(C) Determine the represented value of estimated annual operating
cost for cooling-only units or the cooling portion of the estimated
annual operating cost for air-source heat pumps that provide both
heating and cooling by calculating the product of:
(1) The quotient of the represented value of cooling capacity, in
Btu's per hour as determined in paragraph (a)(1)(iii)(A)(3) of this
section, divided by the represented value of SEER, in Btu's per watt-
hour, as determined in paragraph (a)(1)(iii)(A)(2) of this section;
(2) The representative average use cycle for cooling of 1,000 hours
per year;
(3) A conversion factor of 0.001 kilowatt per watt; and
(4) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act.
(D) Determine the represented value of estimated annual operating
cost for air-source heat pumps that provide only heating or for the
heating portion of the estimated annual operating cost for air-source
heat pumps that provide both heating and cooling, as follows:
(1) When using appendix M to subpart B of part 430, the product of:
(i) The quotient of the mean of the standardized design heating
requirement for the sample, in Btu's per hour, nearest to the Region IV
minimum design heating requirement, determined for each unit in the
sample in section 4.2 of appendix M to subpart B of part 430, divided
by the represented value of heating seasonal performance factor (HSPF),
in Btu's per watt-hour, calculated for Region IV corresponding to the
above-mentioned standardized design heating requirement, as determined
in paragraph (a)(1)(iii)(A)(2) of this section;
(ii) The representative average use cycle for heating of 2,080
hours per year;
(iii) The adjustment factor of 0.77, which serves to adjust the
calculated design heating requirement and heating load hours to the
actual load experienced by a heating system;
(iv) A conversion factor of 0.001 kilowatt per watt; and
(v) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act;
and
(2) When using appendix M1 to subpart B of part 430, the product
of:
(i) The quotient of the represented value of cooling capacity (for
air-source heat pumps that provide both cooling and heating) in Btu's
per hour, as determined in paragraph (a)(1)(iii)(A)(3) of this section,
or the represented value of heating capacity (for air-source heat pumps
that provide only heating), as determined in paragraph
(a)(1)(iii)(A)(4) of this section, divided by the represented value of
heating seasonal performance factor (HSPF), in Btu's per watt-hour,
calculated for Region IV, as determined in paragraph (a)(1)(iii)(A)(2)
of this section;
(ii) The representative average use cycle for heating of 1,572
hours per year;
(iii) The adjustment factor of 1.30, which serves to adjust the
calculated design heating requirement and heating load hours to the
actual load experienced by a heating system;
(iv) A conversion factor of 0.001 kilowatt per watt; and
(v) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act;
(E) Determine the represented value of estimated annual operating
cost for air-source heat pumps that provide both heating and cooling by
calculating the sum of the quantity determined in paragraph
(a)(1)(iii)(C) of this section added to the quantity determined in
paragraph (a)(1)(iii)(D) of this section.
(F) Determine the represented value of estimated regional annual
operating cost for cooling-only units or the cooling portion of the
estimated regional annual operating cost for air-source heat pumps that
provide both heating and cooling by calculating the product of:
(1) The quotient of the represented value of cooling capacity, in
Btu's per hour, determined in paragraph (a)(1)(iii)(A)(3) of this
section divided by the represented value of SEER, in Btu's per watt-
hour, determined in paragraph (a)(1)(iii)(A)(2) of this section;
(2) The estimated number of regional cooling load hours per year
determined from Table 21 in section 4.3.2 of appendix M or Table 20 in
section 4.3.2 of appendix M1, as applicable, to subpart B of part 430;
(3) A conversion factor of 0.001 kilowatts per watt; and
(4) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act.
(G) Determine the represented value of estimated regional annual
operating cost for air-source heat pumps that provide only heating or
for the heating
[[Page 69338]]
portion of the estimated regional annual operating cost for air-source
heat pumps that provide both heating and cooling as follows:
(1) When using Appendix M to subpart B of Part 430, the product of:
(i) The estimated number of regional heating load hours per year
determined from Table 21 in section 4.3.2 of appendix M to subpart B of
part 430;
(ii) The quotient of the mean of the standardized design heating
requirement for the sample, in Btu's per hour, for the appropriate
generalized climatic region of interest (i.e., corresponding to the
regional heating load hours from ``A'') and determined for each unit in
the sample in section 4.2 of appendix M to subpart B of Part 430,
divided by the represented value of HSPF, in Btu's per watt-hour,
calculated for the appropriate generalized climatic region of interest
and corresponding to the above-mentioned standardized design heating
requirement, and determined in paragraph (a)(1)(iii)(A)(2);
(iii) The adjustment factor of 0.77; which serves to adjust the
calculated design heating requirement and heating load hours to the
actual load experienced by a heating system;
(iv) A conversion factor of 0.001 kilowatts per watt; and
(v) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act;
and
(2) When using Appendix M1 to subpart B of Part 430, the product
of:
(i) The estimated number of regional heating load hours per year
determined from Table 20 in section 4.2 of appendix M1 to subpart B of
Part 430;
(ii) The quotient of the represented value of cooling capacity (for
air-source heat pumps that provide both cooling and heating) in Btu's
per hour, as determined in section (a)(1)(iii)(A)(3), or the
represented value of heating capacity (for air-source heat pumps that
provide only heating), as determined in section (a)(1)(iii)(A)(4),
divided by the represented value of HSPF, in Btu's per watt-hour,
calculated for the appropriate generalized climatic region of interest,
and determined in (a)(1)(iii)(A)(2);
(iii) The adjustment factor of 1.30, which serves to adjust the
calculated design heating requirement and heating load hours to the
actual load experienced by a heating system;
(iv) A conversion factor of 0.001 kilowatts per watt; and
(v) The representative average unit cost of electricity in dollars
per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act.
(H) For air-source heat pumps that provide both heating and
cooling, the estimated regional annual operating cost is the sum of the
quantity determined in paragraph (a)(1)(iii)(F) of this section added
to the quantity determined in paragraph (a)(1)(iii)(G) of this section.
(I) The cooling mode efficiency measure for cooling-only units and
for air-source heat pumps that provide cooling is the represented value
of the SEER, in Btu's per watt-hour, pursuant to paragraph
(a)(1)(iii)(A)(2) of this section.
(J) The heating mode efficiency measure for air-source heat pumps
is the represented value of the HSPF, in Btu's per watt-hour for each
applicable standardized design heating requirement within each climatic
region, pursuant to paragraph (a)(1)(iii)(A)(2) of this section.
(K) Round represented values of estimated annual operating cost to
the nearest dollar per year. Round represented values of EER, SEER,
HSPF, and APF to the nearest 0.05. Round represented values of off-mode
power consumption, pursuant to paragraph (a)(1)(iii)(A)(1) to the
nearest watt.
(2) Units not required to be tested.
(i) For basic models rated by ICMs and single-split-system air
conditioners, split-system heat pumps, space-constrained split-system
heat pumps, and space-constrained split-system air conditioners. For
every individual combination within a basic model other than the
individual combination required to be tested pursuant to paragraph
(a)(1)(ii) of this section, either:
(A) A sample of sufficient size, comprised of production units or
representing production units, must be tested as complete systems with
the resulting ratings for the combination obtained in accordance with
paragraphs (a)(1)(i) and (iii) of this section; or
(B) The representative values of the measures of energy efficiency
must be assigned through the application of an AEDM in accordance with
paragraph (a)(3) of this section and Sec. 429.70. An AEDM may only be
used to rate individual combinations in a basic model other than the
combination required for mandatory testing under paragraph (a)(1)(ii)
of this section. No basic model may be rated with an AEDM.
(ii) For multi-split systems, multi-circuit systems, and single-
zone-multiple-coil systems. The following applies:
(A) For basic models composed of both non-ducted and short-ducted
units, the represented value for the mixed non-ducted/short-ducted
combination is the mean of the represented values for the non-ducted
and short-ducted combinations as determined in accordance with
paragraph (a)(1)(iii)(A) of this section.
(B) All other individual combinations of models of indoor units for
the same model of outdoor unit for which the manufacturer chooses to
make representations must be rated as a different basic model, and the
provisions of (a)(1)(i) through (a)(1)(iii) and (a)(2)(ii)(A) of this
section apply.
(3) Alternative efficiency determination methods. In lieu of
testing, represented values of efficiency or consumption may be
determined through the application of an AEDM pursuant to the
requirements of Sec. 429.70 and the provisions of this section.
(i) Power or energy consumption. Any represented value of the
average off mode power consumption or other measure of energy
consumption of an individual combination for which consumers would
favor lower values must be greater than or equal to the output of the
AEDM.
(ii) Energy efficiency. Any represented value of the SEER, EER,
HSPF or other measure of energy efficiency of an individual combination
for which consumers would favor higher values must be less than or
equal to the output of the AEDM.
(b) Limitations. The following section explains the limitations for
certification of models.
(1) Regional. Any model of outdoor unit that is certified in a
combination that does not meet all regional standards cannot also be
certified in a combination that meets the regional standard(s). Outdoor
unit model numbers cannot span regions unless the model of outdoor unit
is compliant with all standards in all possible combinations. If a
model of outdoor unit is certified below a regional standard, then it
must have a unique individual model number for distribution in each
region.
(2) Multiple product classes. Models of outdoor units that are
rated and distributed in combinations that span multiple product
classes must be tested and certified pursuant to paragraph (a) as
compliant with the applicable standard for each product class.
(c) Certification reports. This paragraph specifies the information
that must be included in a certification report.
(1) General. The requirements of Sec. 429.12 apply to central air
conditioners and heat pumps.
(2) Public product-specific information. Pursuant to Sec.
429.12(b)(13), for each basic model (for single-package systems) or
individual combination (for split-systems), a certification report
[[Page 69339]]
must include the following public product-specific information: The
seasonal energy efficiency ratio (SEER in British thermal units per
Watt-hour (Btu/W-h)); the average off mode power consumption
(PW,OFF in Watts); the cooling capacity in British thermal
units per hour (Btu/h); the sensible heat ratio calculated based on
full-load cooling conditions at the outdoor ambient conditions of 82
[deg]F dry bulb and 65 [deg]F wet bulb; and
(i) For heat pumps, the heating seasonal performance factor (HSPF
in British thermal units per Watt-hour (Btu/W-h));
(ii) For air conditioners (excluding space constrained), the energy
efficiency ratio (EER in British thermal units per Watt-hour (Btu/W-
h));
(iii) For single-split-system equipment, whether the rating is for
a coil-only or blower coil system; and
(iv) For multi-split, multiple-circuit, and single-zone-multiple-
coil systems (including VRF), whether the rating is for a non-ducted,
short-ducted, SDHV, or mixed non-ducted and short-ducted system.
(3) Basic and individual model numbers. The basic model number and
individual model number(s) required to be reported under Sec.
429.12(b)(6) must consist of the following:
----------------------------------------------------------------------------------------------------------------
Individual model No(s).
Equipment type Basic model No. -----------------------------------------------------------
1 2 3
----------------------------------------------------------------------------------------------------------------
Single Package.................. Number unique to Package........... N/A............... N/A.
the basic model.
Split System (rated by OUM)..... Number unique to Outdoor Unit...... Indoor Unit(s).... Air Mover (or N/A
the basic model. if rating coil-
only system or
fan is part of
indoor unit model
number).
Outdoor Unit Only............... Number unique to Outdoor Unit...... N/A............... N/A.
the basic model.
Split-System or SDHV (rated by Number unique to Outdoor Unit...... Indoor Unit(s).... N/A.
ICM). the basic model.
----------------------------------------------------------------------------------------------------------------
(4) Additional product-specific information. Pursuant to Sec.
429.12(b)(13), for each individual model/combination, a certification
report must include the following additional product-specific
information: The cooling full load air volume rate for the system or
for each indoor unit as applicable (in cubic feet per minute (cfm));
the air volume rates for other test conditions including minimum
cooling air volume rate, intermediate cooling air volume rate, full
load heating air volume rate, minimum heating air volume rate,
intermediate heating air volume rate, and nominal heating air volume
rate (cfm) for the system or for each indoor unit as applicable, if
different from the cooling full load air volume rate; whether the
individual model uses a fixed orifice, thermostatic expansion valve,
electronic expansion valve, or other type of metering device; the
duration of the compressor break-in period, if used; the Cc value used
to represent cooling mode cycling losses; the temperatures at which the
crankcase heater with controls is designed to turn on and designed to
turn off for the heating season, if applicable; the duration of the
crankcase heater time delay for the shoulder season and heating season,
if such time delay is employed; the maximum time between defrosts as
allowed by the controls (in hours); whether an inlet plenum was
installed during testing; and
(i) For heat pumps, the Ch value used;
(ii) For multi-split, multiple-circuit, and single-zone-multiple-
coil systems, the number of indoor units tested with the outdoor unit;
the nominal cooling capacity of each indoor unit and outdoor unit in
the combination; and the indoor units that are not providing heating or
cooling for part-load tests;
(iii) For ducted systems having multiple indoor fans within a
single indoor unit, the number of indoor fans; the nominal cooling
capacity of the indoor unit and outdoor unit; which fan(s) are
operating to attain the full-load air volume rate when controls limit
the simultaneous operation of all fans within the single indoor unit;
and the allocation of the full-load air volume rate to each operational
fan when different capacity blowers are connected to the common duct;
(iv) For models tested with an indoor blower installed, the
airflow-control settings associated with full load cooling operation;
and the airflow-control settings or alternative instructions for
setting fan speed to the speed upon which the rating is based;
(v) For models with time-adaptive defrost control, the frosting
interval to be used during Frost Accumulation tests and the procedure
for manually initiating the defrost at the specified time;
(vi) For models of indoor units designed for both horizontal and
vertical installation or for both up-flow and down-flow vertical
installations, the orientation used for testing;
(vii) For variable speed units, the compressor frequency set
points, and the required dip switch/control settings for step or
variable components; and
(viii) For variable speed heat pumps, whether the unit controls
restrict use of minimum compressor speed operation for some range of
operating ambient conditions, whether the unit controls restrict use of
maximum compressor speed operation for any ambient temperatures below
17 [deg]F, and whether the optional H42 low temperature test
was used to characterize performance at temperatures below 17 [deg]F.
(d) Alternative efficiency determination methods. Alternative
methods for determining efficiency or energy use for central air
conditioners and heat pumps can be found in Sec. 429.70(e) of this
subpart.
0
4. Amend Sec. 429.70 by revising paragraph (e) to read as follows:
Sec. 429.70 Alternative methods for determining energy efficiency or
energy use.
* * * * *
(e) Alternate Efficiency Determination Method (AEDM) for central
air conditioners and heat pumps. This paragraph sets forth the
requirements for a manufacturer to use an AEDM to rate central air
conditioners and heat pumps
(1) Criteria an AEDM must satisfy. A manufacturer may not apply an
AEDM to an individual combination to determine its certified ratings
(SEER, EER, HSPF, and/or PW,OFF) pursuant to this section
unless authorized pursuant to Sec. 429.16(a)(2) and:
(i) The AEDM is derived from a mathematical model that estimates
the energy efficiency or energy
[[Page 69340]]
consumption characteristics of the individual combination (SEER, EER,
HSPF, and/or PW,OFF) as measured by the applicable DOE test
procedure; and
(ii) The manufacturer has validated the AEDM in accordance with
paragraph (e)(2) of this section and using individual combinations that
meet the current Federal energy conservation standards.
(2) Validation of an AEDM. Before using an AEDM, the manufacturer
must validate the AEDM's accuracy and reliability as follows:
(i) The manufacturer must complete testing of each basic model as
required under Sec. 429.16(a)(1)(ii). Using the AEDM, calculate the
energy use or efficiency for each of the tested individual combinations
within each basic model. Compare the rating based on testing and the
AEDM energy use or efficiency output according to paragraph (e)(2)(ii)
of this section. The manufacturer is responsible for ensuring the
accuracy and reliability of the AEDM.
(ii) Individual combination tolerances. This paragraph provides the
tolerances applicable to individual combinations rated using an AEDM.
(A) For an energy-efficiency metric, the predicted efficiency for
each individual combination calculated by applying the AEDM may not be
more than three percent greater than the efficiency determined from the
corresponding test of the combination.
(B) For an energy-consumption metric, the predicted energy
consumption for each individual combination, calculated by applying the
AEDM, may not be more than three percent less than the energy
consumption determined from the corresponding test of the combination.
(C) The predicted energy efficiency or consumption for each
individual combination calculated by applying the AEDM must meet or
exceed the applicable federal energy conservation standard.
(iii) Additional test unit requirements. Each test must have been
performed in accordance with the DOE test procedure applicable at the
time the individual combination being rated with the AEDM is
distributed in commerce.
(3) AEDM records retention requirements. If a manufacturer has used
an AEDM to determine representative values pursuant to this section,
the manufacturer must have available upon request for inspection by the
Department records showing:
(i) The AEDM, including the mathematical model, the engineering or
statistical analysis, and/or computer simulation or modeling that is
the basis of the AEDM;
(ii) Product information, complete test data, AEDM calculations,
and the statistical comparisons from the units tested that were used to
validate the AEDM pursuant to paragraph (e)(2) of this section; and
(iii) Product information and AEDM calculations for each individual
combination certified using the AEDM.
(4) Additional AEDM requirements. If requested by the Department
and at DOE's discretion, the manufacturer must perform at least one of
the following:
(i) Conduct simulations before representatives of the Department to
predict the performance of particular individual combinations; or
(ii) Provide analyses of previous simulations conducted by the
manufacturer; or
(iii) Conduct certification testing of individual combinations
selected by the Department.
(5) AEDM verification testing. DOE may use the test data for a
given individual combination generated pursuant to Sec. 429.104 to
verify the certified rating determined by an AEDM as long as the
following process is followed:
(i) Selection of units. DOE will obtain one or more units for test
from retail, if available. If units cannot be obtained from retail, DOE
will request that a unit be provided by the manufacturer;
(ii) Lab requirements. DOE will conduct testing at an independent,
third-party testing facility of its choosing. In cases where no third-
party laboratory is capable of testing the equipment, testing may be
conducted at a manufacturer's facility upon DOE's request.
(iii) Testing. At no time during verification testing may the lab
and the manufacturer communicate without DOE authorization. If during
test set-up or testing, the lab indicates to DOE that it needs
additional information regarding a given individual combination in
order to test in accordance with the applicable DOE test procedure, DOE
may organize a meeting between DOE, the manufacturer and the lab to
provide such information.
(iv) Failure to meet certified rating. If an individual combination
tests worse than its certified rating (i.e., lower than the certified
efficiency rating or higher than the certified consumption rating) by
more than 5%, or the test results in a different cooling capacity than
its certified cooling capacity by more than 5%, DOE will notify the
manufacturer. DOE will provide the manufacturer with all documentation
related to the test set up, test conditions, and test results for the
unit. Within the timeframe allotted by DOE, the manufacturer:
(A) May present any and all claims regarding testing validity; and
(B) If not on site for the initial test set-up, must test at least
one additional unit of the same combination obtained from a retail
source at its own expense, following the test requirements in Sec.
429.110(a)(3). When testing at an independent lab, the manufacturer may
choose to have DOE and the manufacturer present.
(v) Tolerances. This subparagraph specifies the tolerances DOE will
permit when conducting verification testing.
(A) For consumption metrics, the result from a DOE verification
test must be less than or equal to 1.05 multiplied by the certified
rating.
(B) For efficiency metrics, the result from a DOE verification test
must be greater than or equal to 1.05 multiplied by the certified
rating.
(vi) Invalid rating. If, following discussions with the
manufacturer and a retest where applicable, DOE determines that the
verification testing was conducted appropriately in accordance with the
DOE test procedure, DOE will issue a determination that the ratings for
the basic model are invalid. The manufacturer must conduct additional
testing and re-rate and re-certify the individual combinations within
the basic model that were rated using the AEDM based on all test data
collected, including DOE's test data.
(vii) AEDM use. This subparagraph specifies when a manufacturer's
use of an AEDM may be restricted due to prior invalid ratings.
(A) If DOE has determined that a manufacturer made invalid ratings
on individual combinations within two or more basic models rated using
the manufacturer's AEDM within a 24 month period, the manufacturer must
test the least efficient and most efficient combination within each
basic model in addition to the combination specified in Sec.
429.16(a)(1)(ii). The twenty-four month period begins with a DOE
determination that a rating is invalid through the process outlined
above.
(B) If DOE has determined that a manufacturer made invalid ratings
on more than four basic models rated using the manufacturer's AEDM
within a 24-month period, the manufacturer may no longer use an AEDM.
(C) If a manufacturer has lost the privilege of using an AEDM, the
manufacturer may regain the ability to use an AEDM by:
(1) Investigating and identifying cause(s) for failures;
[[Page 69341]]
(2) Taking corrective action to address cause(s);
(3) Performing six new tests per basic model, a minimum of two of
which must be performed by an independent, third-party laboratory from
units obtained from retail to validate the AEDM; and
(4) Obtaining DOE authorization to resume use of an AEDM.
* * * * *
0
5. Amend Sec. 429.134 by adding paragraph (g) to read as follows:
Sec. 429.134 Product-specific enforcement provisions.
* * * * *
(g) Central air conditioners and heat pumps.--(1) Verification of
cooling capacity. The cooling capacity of each tested unit of the basic
model (for single package systems) or individual combination (for
split-systems) will be measured pursuant to the test requirements of
Sec. 430.23(m). The results of the measurement(s) will be compared to
the value of cooling capacity certified by the manufacturer.
(i) If the measurement(s) (either the measured cooling capacity for
a single unit sample or the average of the measured cooling capacities
for a multiple unit sample) is less than or equal to 1.05 multiplied by
the certified cooling capacity and greater than or equal to 0.95
multiplied by the certified cooling capacity, the certified cooling
capacity will be used as the basis for determining SEER.
(ii) Otherwise, the measurement(s) (either the measured cooling
capacity for a single unit sample or the average of the measured
cooling capacities for a multiple unit sample, as applicable) will be
used as the basis for determining SEER.
(2) Verification of CD value--(i) For central air conditioners and
heat pumps other than models of outdoor units with no match, the Cc
and/or Ch value of the basic model (for single package systems) or
individual combination (for split-systems), as applicable, will be
measured pursuant to the test requirements of Sec. 430.23(m) for each
unit tested. The results of the measurement(s) for each Cc or Ch value
will be compared to the Cc or Ch value certified by the manufacturer.
(A) If the results of the measurement(s) (either the measured value
for a single unit sample or the average of the measured values for a
multiple unit sample) is 0.02 or more greater than the certified Cc or
Ch value, the average measured Cc or Ch value will serve as the basis
for calculation of SEER or HSPF for the basic model/individual
combination.
(B) For all other cases, the certified Cc or Ch value will be used
as the basis for calculation of SEER or HSPF for the basic model/
individual combination.
(ii) For models of outdoor units with no match, or for tests in
which the criteria for the cyclic test in 10 CFR part 430, subpart B,
Appendix M or M1, as applicable, section 3.5e, cannot be achieved, DOE
will use the default Cc and/or Ch value pursuant to 10 CFR part 430.
PART 430--ENERGY CONSERVATION PROGRAM FOR CONSUMER PRODUCTS
0
6. The authority citation for part 430 continues to read as follows:
Authority: 42 U.S.C. 6291-6309; 28 U.S.C. 2461 note.
0
7. Section 430.2 is amended by:
0
a. Removing the definitions of ``ARM/simulation adjustment factor,''
``coil family,'' ``condenser-evaporator coil combination'',
``condensing unit,'' ``evaporator coil'', ``heat pump,'' ``indoor
unit,'' ``outdoor unit,'' ``small duct, high velocity system,'' and
``tested combination;'' and
0
b. Revising the definitions of ``basic model;'' and ``central air
conditioner'' to read as follows:
Sec. 430.2 Definitions.
* * * * *
Basic model means all units of a given type of covered product (or
class thereof) manufactured by one manufacturer; having the same
primary energy source; and, which have essentially identical
electrical, physical, and functional (or hydraulic) characteristics
that affect energy consumption, energy efficiency, water consumption,
or water efficiency; and
(1) With respect to general service fluorescent lamps, general
service incandescent lamps, and incandescent reflector lamps: Lamps
that have essentially identical light output and electrical
characteristics--including lumens per watt (lm/W) and color rendering
index (CRI).
(2) With respect to faucets and showerheads: Have the identical
flow control mechanism attached to or installed within the fixture
fittings, or the identical water-passage design features that use the
same path of water in the highest flow mode.
(3) With respect to furnace fans: Are marketed and/or designed to
be installed in the same type of installation; and
(4) With respect to central air conditioners and central air
conditioning heat pumps:
(i) Essentially identical electrical, physical, and functional (or
hydraulic) characteristics means:
(A) For split-systems manufactured by independent coil
manufacturers (ICMs) and for small-duct, high velocity systems: All
individual combinations having the same model of indoor unit, which
means the same or comparably performing indoor coil(s) [same face area;
fin material, depth, style (e.g., wavy, louvered), and density (fins
per inch); tube pattern, material, diameter, wall thickness, and
internal enhancement], indoor blower(s) [same air flow with the same
indoor coil and external static pressure, same power input], auxiliary
refrigeration system components if present (e.g., expansion valve), and
controls.
(B) for split-systems manufactured by outdoor unit manufacturers
(OUMs): All individual combinations having the same model of outdoor
unit, which means the same or comparably performing compressor(s) [same
displacement rate (volume per time) and same capacity and power input
when tested under the same operating conditions], outdoor coil(s) [same
face area; fin material, depth, style (e.g., wavy, louvered), and
density (fins per inch); tube pattern, material, diameter, wall
thickness, and internal enhancement], outdoor fan(s) [same air flow
with the same outdoor coil, same power input], auxiliary refrigeration
system components if present (e.g., suction accumulator, reversing
valve, expansion valve), and controls.
(C) for single-package models: All individual models having the
same or comparably performing compressor(s) [same displacement rate
(volume per time) and same capacity and power input when tested under
the same operating conditions], outdoor coil(s) and indoor coil(s)
[same face area; fin material, depth, style (e.g., wavy, louvered), and
density (fins per inch); tube pattern, material, diameter, wall
thickness, and internal enhancement], outdoor fan(s) [same air flow
with the same outdoor coil, same power input], indoor blower(s) [same
air flow with the same indoor coil and external static pressure, same
power input], auxiliary refrigeration system components if present
(e.g. suction accumulator, reversing valve, expansion valve), and
controls.
(ii) For single-split-system and single-package models,
manufacturers may instead choose to make each individual combination or
model its own basic model provided the testing and rating requirements
in 10 CFR 429.16 are met.
(iii) For multi-split, multi-circuit, and single-zone-multiple-coil
models, a
[[Page 69342]]
basic model may not include both individual SDHV combinations and non-
SDHV combinations even when they include the same model of outdoor
unit. The manufacturer may choose to identify specific individual
combinations as additional basic models.
* * * * *
Central air conditioner or central air conditioning heat pump means
a product, other than a packaged terminal air conditioner or packaged
terminal heat pump, which is powered by single phase electric current,
air cooled, rated below 65,000 Btu per hour, not contained within the
same cabinet as a furnace, the rated capacity of which is above 225,000
Btu per hour, and is a heat pump or a cooling unit only. A central air
conditioner or central air conditioning heat pump may consist of: A
single-package unit; an outdoor unit and one or more indoor units; an
indoor unit only; or an outdoor unit only. In the case of an indoor
unit only or an outdoor unity only, the unit must be tested and rated
as a system (combination of both an indoor and an outdoor unit). For
all central air conditioner and central air conditioning heat pump-
related definitions, see appendices M or M1 of subpart B of this part.
0
8. Section 430.3 is amended by:
0
a. Revising paragraphs (c)(1) and (g)(2);
0
b. Adding paragraphs (c)(3) and (c)(4);
0
c. Removing paragraphs (g)(3);
0
d. Redesignating paragraphs (g)(4) through (g)(14) as (g)(3) through
(g)(13); and
0
e. Revising newly redesignated (g)(3) through (g)(9).
The revisions and additions read as follows:
Sec. 430.3 Materials incorporated by reference.
* * * * *
(c) * * *
(1) AHRI 210/240-2008 with Addendums 1 and 2 (formerly ARI Standard
210/240), Performance Rating of Unitary Air-Conditioning & Air-Source
Heat Pump Equipment, sections 6.1.3.2, 6.1.3.4, 6.1.3.5 and figures D1,
D2, D4, approved by ANSI December, 2012, IBR approved for appendix M
and M1 to subpart B.
* * * * *
(3) ANSI/AHRI 1230-2010 with Addendum 2, Performance Rating of
Variable Refrigerant Flow Multi-Split Air-Conditioning and Heat Pump
Equipment, sections 3 (except 3.8, 3.9, 3.13, 3.14, 3.15, 3.16, 3.23,
3.24, 3.26, 3.27, 3.28, 3.29, 3.30, and 3.31), 5.1.3, 5.1.4, 6.1.5
(except Table 8), 6.1.6, and 6.2, approved August 2, 2010, Addendum 2
dated June 2014, IBR approved for appendices M and M1 to subpart B.
(4) AHRI 210/240-Draft, Performance Rating of Unitary Air-
Conditioning & Air-Source Heat Pump Equipment, appendix E, section E4,
Docket No. EERE-2009-BT-TP-0004 No. 45.
* * * * *
(g) * * *
(2) ASHRAE 23.1-2010, Methods of Testing for Rating the Performance
of Positive Displacement Refrigerant Compressors and Condensing Units
that Operate at Subcritical Temperatures of the Refrigerant, sections
5, 6, 7, and 8 only, approved January 28, 2010, IBR approved for
appendices M and M1 to subpart B.
(3) ASHRAE 37-2009, Methods of Testing for Rating Electrically
Driven Unitary Air-Conditioning and Heat Pump Equipment, approved June
25, 2009, IBR approved for appendix AA subpart to B. Sections 5.1.1,
5.2, 5.5.1, 6.1.1, 6.1.2, 6.1.4, 6.4, 6.5, 7.3, 7.4, 7.5, 7.7.2.1,
7.7.2.2, 8.1.2, 8.1.3, 8.2, 8.6.2; figures 1, 2, 4, 7a, 7b, 7c, 8; and
table 3 only IBR approved for appendices M and M1 to subpart B.
* * * * *
(4) ASHRAE 41.1-1986 (Reaffirmed 2006), Standard Method for
Temperature Measurement, approved February 18, 1987, IBR approved for
appendices E and AA to subpart B.
(5) ASHRAE 41.1-2013, Standard Method for Temperature Measurement,
approved January 30, 2013, IBR approved for appendix X1 to subpart B.
Sections 4, 5, 6, 7.2, and 7.3 only, IBR approved for appendices M and
M1 to subpart B.
(6) ASHRAE 41.2-1987 (Reaffirmed 1992), Standard Methods for
Laboratory Airflow Measurement, section 5.2.2 and figure 14, approved
October 1, 1987, IBR approved for appendices M and M1 to subpart B.
(7) ASHRAE 41.6-2014, Standard Method for Humidity Measurement,
sections 4, 5, 6, and 7.1, approved July 3, 2014, sections 4, 5, 6, and
7 only IBR approved for appendices M and M1 to subpart B.
(8) ASHRAE 41.9-2011, Standard Methods for Volatile-Refrigerant
Mass Flow Measurements Using Calorimeters, approved February 3, 2011,
sections 5, 6, 7, 8, 9, and 11 only IBR approved for appendices M and
M1 to subpart B.
(9) ASHRAE/AMCA 51-07/210-07, Laboratory Methods of Testing Fans
for Certified Aerodynamic Performance Rating, figures 2A and 12,
approved August 17, 2007, IBR approved for appendices M and M1 to
subpart B.
* * * * *
0
9. Section 430.23 is amended by revising paragraph (m) to read as
follows:
Sec. 430.23 Test procedures for the measurement of energy and water
consumption.
* * * * *
(m) Central air conditioners and heat pumps. See the note at the
beginning of appendix M and M1 to determine the appropriate test
method. All values discussed in this section must be determined using a
single appendix.
(1) Cooling capacity must be determined from the steady-state wet-
coil test (A or A2 Test), as described in section 3.2 of appendix M or
M1 to this subpart, and rounded off to the nearest (i) to the nearest
50 Btu/h if cooling capacity is less than 20,000 Btu/h, (ii) to the
nearest 100 Btu/h if cooling capacity is greater than or equal to
20,000 Btu/h but less than 38,000 Btu/h, and (iii) to the nearest 250
Btu/h if cooling capacity is greater than or equal to 38,000 Btu/h and
less than 65,000 Btu/h.
(2) Seasonal energy efficiency ratio (SEER) must be determined from
section 4.1 of appendix M or M1 to this subpart, and rounded off to the
nearest 0.025 Btu/W-h.
(3) When representations are made of energy efficiency ratio (EER),
EER must be determined in section 4.7 of appendix M or M1 to this
subpart, and rounded off to the nearest 0.025 Btu/W-h.
(4) Heating seasonal performance factors (HSPF) must be determined
in section 4.2 of appendix M or M1 to this subpart, and rounded off to
the nearest 0.025 Btu/W-h.
(5) Average off mode power consumption must be determined according
to section 4.3 of appendix M or M1 to this subpart, and rounded off to
the nearest 0.5 W.
(6) Sensible heat ratio (SHR) must be determined according to
section 4.6 of appendix M or M1 to this subpart, and rounded off to the
nearest 0.5 percent (%).
(7) All other measures of energy efficiency or consumption or other
useful measures of performance must be determined using appendix M or
M1 of this subpart.
* * * * *
0
10. Revise appendix M to subpart B of part 430 to read as follows:
[[Page 69343]]
APPENDIX M TO SUBPART B OF PART 430--UNIFORM TEST METHOD FOR MEASURING
THE ENERGY CONSUMPTION OF CENTRAL AIR CONDITIONERS AND HEAT PUMPS
Note: Prior to May 9, 2016, any representations, including
compliance certifications, made with respect to the energy use,
power, or efficiency of central air conditioners and central air
conditioning heat pumps must be based on the results of testing
pursuant to either this appendix or the procedures in Appendix M as
it appeared at 10 CFR part 430, subpart B, Appendix M, in the 10 CFR
parts 200 to 499 edition revised as of January 1, 2015. Any
representations made with respect to the energy use or efficiency of
such central air conditioners and central air conditioning heat
pumps must be in accordance with whichever version is selected.
On or after May 9, 2016 and prior to the compliance date for any
amended energy conservation standards, any representations, including
compliance certifications, made with respect to the energy use, power,
or efficiency of central air conditioners and central air conditioning
heat pumps must be based on the results of testing pursuant to this
appendix.
On or after the compliance date for any amended energy conservation
standards, any representations, including compliance certifications,
made with respect to the energy use, power, or efficiency of central
air conditioners and central air conditioning heat pumps must be based
on the results of testing pursuant to appendix M1 of this subpart.
1. Scope and Definitions
1.1 Scope.
This test procedure provides a method of determining SEER, EER,
HSPF and PW,OFF for central air conditioners and central
air conditioning heat pumps including the following categories:
(a) Split-system air conditioners; and single-zone-multiple-
coil, multi-split (including VRF), and multi-circuit systems
(b) Split-system heat pumps and single-zone-multiple-coil,
multi-split (including VRF), and multi-circuit systems
(c) Single-package air conditioners
(d) Single-package heat pumps
(e) Small-duct, high-velocity systems (including VRF)
(f) Space-constrained products--air conditioners
(g) Space-constrained products--heat pumps
For purposes of this appendix, the Department of Energy
incorporates by reference specific sections of several industry
standards, as listed in Sec. 430.3. In cases where there is a
conflict, the language of the test procedure in this appendix takes
precedence over the incorporated standards.
All section references refer to sections within this appendix
unless otherwise stated.
1.2 Definitions.
Airflow-control settings are programmed or wired control system
configurations that control a fan to achieve discrete, differing
ranges of airflow--often designated for performing a specific
function (e.g., cooling, heating, or constant circulation)--without
manual adjustment other than interaction with a user-operable
control (i.e., a thermostat) that meets the manufacturer
specifications for installed-use. For the purposes of this appendix,
manufacturer specifications for installed-use are those found in the
product literature shipped with the unit.
Airflow prevention device denotes a device(s) that prevents
airflow via natural convection by mechanical means, such as an air
damper box, or by means of changes in duct height, such as an
upturned duct.
Annual performance factor means the total heating and cooling
done by a heat pump in a particular region in one year divided by
the total electric energy used in one year.
Blower coil indoor unit means the indoor unit of a split-system
central air conditioner or heat pump that includes a refrigerant-to-
air heat exchanger coil, may include a cooling-mode expansion
device, and includes either an indoor blower housed with the coil or
a separate designated air mover such as a furnace or a modular
blower (as defined in Appendix AA to the subpart). Blower coil
system refers to a split-system that includes one or more blower
coil indoor units.
CFR means Code of Federal Regulations.
Coefficient of Performance (COP) means the ratio of the average
rate of space heating delivered to the average rate of electrical
energy consumed by the heat pump. These rate quantities must be
determined from a single test or, if derived via interpolation, must
be determined at a single set of operating conditions. COP is a
dimensionless quantity. When determined for a ducted unit tested
without an indoor blower installed, COP must include the section 3.7
and 3.9.1 default values for the heat output and power input of a
fan motor.
Coil-only indoor unit means the indoor unit of a split-system
central air conditioner or heat pump that includes a refrigerant-to-
air heat exchanger coil and may include a cooling-mode expansion
device, but does not include an indoor blower housed with the coil,
and does not include a separate designated air mover such as a
furnace or a modular blower (as defined in Appendix AA to this
subpart. A coil-only indoor unit is designed to use a separately-
installed furnace or a modular blower for indoor air movement. Coil-
only system refers to a system that includes one or more coil-only
indoor units.
Condensing unit removes the heat absorbed by the refrigerant to
transfer it to the outside environment, and which consists of an
outdoor coil, compressor(s), and air moving device.
Constant-air-volume-rate indoor blower means a fan that varies
its operating speed to provide a fixed air-volume-rate from a ducted
system.
Continuously recorded, when referring to a dry bulb measurement,
dry bulb temperature used for test room control, wet bulb
temperature, dew point temperature, or relative humidity
measurements, means that the specified value must be sampled at
regular intervals that are equal to or less than 5 seconds
Cooling load factor (CLF) means the ratio having as its
numerator the total cooling delivered during a cyclic operating
interval consisting of one ON period and one OFF period. The
denominator is the total cooling that would be delivered, given the
same ambient conditions, had the unit operated continuously at its
steady-state, space-cooling capacity for the same total time (ON +
OFF) interval.
Crankcase heater means any electrically powered device or
mechanism for intentionally generating heat within and/or around the
compressor sump volume often done to minimize the dilution of the
compressor's refrigerant oil by condensed refrigerant. Crankcase
heater control may be achieved using a timer or may be based on a
change in temperature or some other measurable parameter, such that
the crankcase heater is not required to operate continuously. A
crankcase heater without controls operates continuously when the
compressor is not operating.
Cyclic Test means a test where the unit's compressor is cycled
on and off for specific time intervals. A cyclic test provides half
the information needed to calculate a degradation coefficient.
Damper box means a short section of duct having an air damper
that meets the performance requirements of section 2.5.7.
Degradation coefficient (CD) means a parameter used
in calculating the part load factor. The degradation coefficient for
cooling is denoted by CDc. The degradation
coefficient for heating is denoted by CDh.
Demand-defrost control system means a system that defrosts the
heat pump outdoor coil only when measuring a predetermined
degradation of performance. The heat pump's controls monitor one or
more parameters that always vary with the amount of frost
accumulated on the outdoor coil (e.g., coil to air differential
temperature, coil differential air pressure, outdoor fan power or
current, optical sensors) at least once for every ten minutes of
compressor ON-time when space heating. One acceptable alternative to
the criterion given in the prior sentence is a feedback system that
measures the length of the defrost period and adjusts defrost
frequency accordingly. In all cases, when the frost parameter(s)
reaches a predetermined value, the system initiates a defrost. In a
demand-defrost control system, defrosts are terminated based on
monitoring a parameter(s) that indicates that frost has been
eliminated from the coil. (Note: Systems that vary defrost intervals
according to outdoor dry-bulb temperature are not demand-defrost
systems.) A demand-defrost control system, which otherwise meets the
above requirements, may allow time-initiated defrosts if, and only
if, such defrosts occur after 6 hours of compressor operating time.
Design heating requirement (DHR) predicts the space heating load
of a residence when subjected to outdoor design conditions.
Estimates for the minimum and maximum
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DHR are provided for six generalized U.S. climatic regions in
section 4.2.
Dry-coil tests are cooling mode tests where the wet-bulb
temperature of the air supplied to the indoor coil is maintained low
enough that no condensate forms on this coil.
Ducted system means an air conditioner or heat pump that is
designed to be permanently installed equipment and delivers
conditioned air to the indoor space through a duct(s). The air
conditioner or heat pump may be either a split-system or a single-
package unit.
Energy efficiency ratio (EER) means the ratio of the average
rate of space cooling delivered to the average rate of electrical
energy consumed by the air conditioner or heat pump. These rate
quantities must be determined from a single test or, if derived via
interpolation, must be determined at a single set of operating
conditions. EER is expressed in units of
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When determined for a ducted unit tested without an indoor blower
installed, EER must include the section 3.3 and 3.5.1 default values
for the heat output and power input of a fan motor.
Evaporator coil absorbs heat from an enclosed space and
transfers the heat to a refrigerant.
Heat pump means a kind of central air conditioner, which
consists of one or more assemblies, utilizing an indoor conditioning
coil, compressor, and refrigerant-to-outdoor air heat exchanger to
provide air heating, and may also provide air cooling, air
dehumidifying, air humidifying, air circulating, and air cleaning.
Heat pump having a heat comfort controller means equipment that
regulates the operation of the electric resistance elements to
assure that the air temperature leaving the indoor section does not
fall below a specified temperature. This specified temperature is
usually field adjustable. Heat pumps that actively regulate the rate
of electric resistance heating when operating below the balance
point (as the result of a second stage call from the thermostat) but
do not operate to maintain a minimum delivery temperature are not
considered as having a heat comfort controller.
Heating load factor (HLF) means the ratio having as its
numerator the total heating delivered during a cyclic operating
interval consisting of one ON period and one OFF period. The
denominator is the total heating that would be delivered, given the
same ambient conditions, if the unit operated continuously at its
steady-state space heating capacity for the same total time (ON plus
OFF) interval.
Heating season means the months of the year that require
heating, e.g., typically, and roughly, October through April.
Heating seasonal performance factor (HSPF) means the total space
heating required during the space heating season, expressed in
Btu's, divided by the total electrical energy consumed by the heat
pump system during the same season, expressed in watt-hours. The
HSPF used to evaluate compliance with the Energy Conservation
Standards (see 10 CFR 430.32(c)) is based on Region IV, the minimum
standardized design heating requirement, and the sampling plan
stated in 10 CFR 429.16(a).
Independent coil manufacturer (ICM) means a manufacturer that
manufactures indoor units but does not manufacture single-package
units or outdoor units.
Indoor unit transfers heat between the refrigerant and the
indoor air and consists of an indoor coil and casing and may include
a cooling mode expansion device and/or an air moving device.
Multiple-circuit (or multi-circuit) system means a split system
that has one outdoor unit and that has two or more indoor units
installed on two or more refrigeration circuits such that each
refrigeration circuit serves a compressor and one and only one
indoor unit, and refrigerant is not shared from circuit to circuit.
Multiple-split (or multi-split) system means a split system that
has one outdoor unit and two or more indoor coil-only or indoor
blower coil units connected to its other component(s) with a single
refrigerant circuit. The indoor units operate independently and can
condition multiple zones in response to at least two indoor
thermostats or temperature sensors. The outdoor unit operates in
response to independent operation of the indoor units based on
control input of multiple indoor thermostats or temperature sensors,
and/or based on refrigeration circuit sensor input (e.g., suction
pressure).
Nominal capacity means the capacity that is claimed by the
manufacturer in the product name plate. Nominal cooling capacity is
approximate to the air conditioner cooling capacity tested at A or
A2 condition. Nominal heating capacity is approximate to the heat
pump heating capacity tested in H12 test (or the optional H1N test).
Non-ducted system means a split-system central air conditioner
or heat pump that is designed to be permanently installed and that
directly heats or cools air within the conditioned space using one
or more indoor units that are mounted on room walls and/or ceilings.
The system may be of a modular design that allows for combining
multiple outdoor coils and compressors to create one overall system.
Normalized Gross Indoor Fin Surface (NGIFS) means the gross fin
surface area of the indoor unit coil divided by the cooling capacity
measured for the A or A2 Test whichever applies.
Off-mode power consumption means the power consumption when the
unit is connected to its main power source but is neither providing
cooling nor heating to the building it serves.
Off-mode season means, for central air conditioners, the
shoulder season and the entire heating season; and for heat pumps,
the shoulder season only.
Outdoor unit transfers heat between the refrigerant and the
outdoor air, and consists of an outdoor coil, compressor(s), an air
moving device, and in addition for heat pumps, could include a
heating mode expansion device, reversing valve, and defrost
controls.
Outdoor unit manufacturer (OUM) means a manufacturer of single-
package units, outdoor units, and/or both indoor units and outdoor
units.
Part-load factor (PLF) means the ratio of the cyclic energy
efficiency ratio (coefficient of performance) to the steady-state
energy efficiency ratio (coefficient of performance), where both
energy efficiency ratios (coefficients of performance) are
determined based on operation at the same ambient conditions.
Seasonal energy efficiency ratio (SEER) means the total heat
removed from the conditioned space during the annual cooling season,
expressed in Btu's, divided by the total electrical energy consumed
by the central air conditioner or heat pump during the same season,
expressed in watt-hours.
Short ducted system means a ducted split system whose one or
more indoor sections produce greater than zero but no greater than
0.1 inches (of water) of external static pressure when operated at
the full-load air volume not exceeding 450 cfm per rated ton of
cooling.
Shoulder season means the months of the year in between those
months that require cooling and those months that require heating,
e.g., typically, and roughly, April through May, and September
through October.
Single-package unit means any central air conditioner or heat
pump that has all major assemblies enclosed in one cabinet.
Single-split-system means a split system that has one outdoor
unit and that has one indoor coil-only or indoor blower coil unit
connected to its other component(s) with a single refrigeration
circuit.
Single-zone-multiple-coil split system means a split system that
has one outdoor unit and that has two or more indoor units connected
with a single refrigeration circuit. The indoor units operate in
unison in response to a single indoor thermostat.
Small-duct, high-velocity system means a system that contains a
blower and indoor coil combination that is designed for, and
produces, at least 1.2 inches (of water) of external static pressure
when operated at the full-load air volume rate of 220-350 cfm per
rated ton of cooling. When applied in the field, uses high-velocity
room outlets (i.e., generally greater than 1000 fpm) having less
than 6.0 square inches of free area.
Split system means any air conditioner or heat pump that has one
or more of the major assemblies separated from the others. Split-
systems may be either blower coil systems or coil-only systems.
Standard Air means dry air having a mass density of 0.075 lb/
ft\3\.
Steady-state test means a test where the test conditions are
regulated to remain as constant as possible while the unit operates
continuously in the same mode.
Temperature bin means the 5 [deg]F increments that are used to
partition the outdoor dry-bulb temperature ranges of the cooling
(>=65 [deg]F) and heating (<65 [deg]F) seasons.
Test condition tolerance means the maximum permissible
difference between the average value of the measured test parameter
and the specified test condition.
Test operating tolerance means the maximum permissible range
that a measurement may vary over the specified test
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interval. The difference between the maximum and minimum sampled
values must be less than or equal to the specified test operating
tolerance.
Tested combination means a single-zone-multiple-coil, multi-
split, or multi-circuit system having the following features:
(1) The system consists of one outdoor unit with one or more
compressors matched with between two and five indoor units;
(2) The indoor units shall:
(i) Collectively, have a nominal cooling capacity greater than
or equal to 95 percent and less than or equal to 105 percent of the
nominal cooling capacity of the outdoor unit;
(ii) Represent the highest sales volume model family that can
meet the 95 percent nominal cooling capacity of the outdoor unit
[Note: another indoor model family may be used if five indoor units
from the highest sales volume model family do not provide sufficient
capacity to meet the 95 percent threshold level].
(iii) Individually not have a nominal cooling capacity greater
than 50 percent of the nominal cooling capacity of the outdoor unit,
unless the nominal cooling capacity of the outdoor unit is 24,000
Btu/h or less;
(iv) Operate at fan speeds consistent with manufacturer's
specifications; and
(v) All be subject to the same minimum external static pressure
requirement while able to produce the same external static pressure
at the exit of each outlet plenum when connected in a manifold
configuration as required by the test procedure.
(vi) Where referenced, ``nominal cooling capacity'' is to be
interpreted for indoor units as the highest cooling capacity listed
in published product literature for 95 [deg]F outdoor dry bulb
temperature and 80 [deg]F dry bulb, 67 [deg]F wet bulb indoor
conditions, and for outdoor units as the lowest cooling capacity
listed in published product literature for these conditions. If
incomplete or no operating conditions are reported, the highest (for
indoor units) or lowest (for outdoor units) such cooing capacity
shall be used.
Time-adaptive defrost control system is a demand-defrost control
system that measures the length of the prior defrost period(s) and
uses that information to automatically determine when to initiate
the next defrost cycle.
Time-temperature defrost control systems initiate or evaluate
initiating a defrost cycle only when a predetermined cumulative
compressor ON-time is obtained. This predetermined ON-time is
generally a fixed value (e.g., 30, 45, 90 minutes) although it may
vary based on the measured outdoor dry-bulb temperature. The ON-time
counter accumulates if controller measurements (e.g., outdoor
temperature, evaporator temperature) indicate that frost formation
conditions are present, and it is reset/remains at zero at all other
times. In one application of the control scheme, a defrost is
initiated whenever the counter time equals the predetermined ON-
time. The counter is reset when the defrost cycle is completed.
In a second application of the control scheme, one or more
parameters are measured (e.g., air and/or refrigerant temperatures)
at the predetermined, cumulative, compressor ON-time. A defrost is
initiated only if the measured parameter(s) falls within a
predetermined range. The ON-time counter is reset regardless of
whether or not a defrost is initiated. If systems of this second
type use cumulative ON-time intervals of 10 minutes or less, then
the heat pump may qualify as having a demand defrost control system
(see definition).
Triple-capacity, northern heat pump means a heat pump that
provides two stages of cooling and three stages of heating. The two
common stages for both the cooling and heating modes are the low
capacity stage and the high capacity stage. The additional heating
mode stage is the booster capacity stage, which offers the highest
heating capacity output for a given set of ambient operating
conditions.
Triple-split system means a central air conditioner or heat pump
that is composed of three separate components: An outdoor fan coil
section, an indoor blower coil section, and an indoor compressor
section.
Two-capacity (or two-stage) compressor system means a central
air conditioner or heat pump that has a compressor or a group of
compressors operating with only two stages of capacity. For such
systems, low capacity means the compressor(s) operating at low
stage, or at low load test conditions. The low compressor stage for
heating mode tests may be the same or different from the cooling
mode value.
For such systems, high capacity means the compressor(s)
operating at low stage, or at full load test conditions.
Two-capacity, northern heat pump means a heat pump that has a
factory or field-selectable lock-out feature to prevent space
cooling at high-capacity. Two-capacity heat pumps having this
feature will typically have two sets of ratings, one with the
feature disabled and one with the feature enabled. The certified
indoor coil model number should reflect whether the ratings pertain
to the lockout enabled option via the inclusion of an extra
identifier, such as ``+LO''. When testing as a two-capacity,
northern heat pump, the lockout feature must remain enabled for all
tests.
Variable refrigerant flow (VRF) system means a multi-split
system with at least three compressor capacity stages, distributing
refrigerant through a piping network to multiple indoor blower coil
units each capable of individual zone temperature control, through
proprietary zone temperature control devices and a common
communications network. Single-phase VRF systems less than 65,000
Btu/h are a kind of central air conditioners and central air
conditioning heat pumps.
Variable-speed compressor system means a central air conditioner
or heat pump that has a compressor that uses a variable-speed drive
to vary the compressor speed to achieve variable capacities.
For such a system, maximum speed means the maximum operating
speed, measured by RPM or frequency (Hz), that the unit is designed
to operate in cooling mode or heating mode. Maximum speed does not
change with ambient temperature, and it can be different from
cooling mode to heating mode. Maximum speed does not necessarily
mean maximum capacity.
For such systems, minimum speed means the minimum speed,
measured by RPM or frequency (Hz), that the unit is designed to
operate in cooling mode or heating mode. Minimum speed does not
change with ambient temperature, and it can be different from
cooling mode to heating mode. Minimum speed does not necessarily
mean minimum capacity.
Wet-coil test means a test conducted at test conditions that
typically cause water vapor to condense on the test unit evaporator
coil.
2. Testing Overview and Conditions
(A) Test VRF systems using ANSI/AHRI Standard 1230-2010 sections
3 (except 3.8, 3.9, 3.13, 3.14, 3.15, 3.16, 3.23, 3.24, 3.26, 3.27,
3.28, 3.29, 3.30, and 3.31), 5.1.3, 5.1.4, 6.1.5 (except Table 8),
6.1.6, and 6.2 (incorporated by reference, see Sec. 430.3) and
Appendix M. Where ANSI/AHRI Standard 1230-2010 refers to the
Appendix C therein substitute the provisions of this appendix. In
cases where there is a conflict, the language of the test procedure
in this appendix takes precedence over ANSI/AHRI Standard 1230-2010.
For definitions use section 1 of Appendix M and section 3 of
ANSI/AHRI Standard 1230-2010, excluding sections 3.8, 3.9, 3.13,
3.14, 3.15, 3.16, 3.23, 3.24, 3.26, 3.27, 3.28, 3.29, 3.30, and
3.31. For rounding requirements refer to Sec. 430.23 (m). For
determination of certified rating requirements refer to Sec.
429.16.
For test room requirements, refer to section 2.1 from Appendix
M. For test unit installation requirements refer to sections 2.2.a,
2.2.b, 2.2.c, 2.2.1, 2.2.2, 2.2.3(a), 2.2.3(c), 2.2.4, 2.2.5, and
2.4 to 2.12 from Appendix M, and sections 5.1.3 and 5.1.4 of ANSI/
AHRI Standard 1230-2010.
For general requirements for the test procedure refer to section
3.1 of Appendix M, except for sections 3.1.3 and 3.1.4, which are
requirements for indoor air volume and outdoor air volume. For
indoor air volume and outdoor air volume requirements, refer instead
to section 6.1.5 (except Table 8) and 6.1.6 of ANSI/AHRI Standard
1230-2010. For external static pressure requirements, refer to Table
3 in Appendix M.
For the test procedure, refer to sections 3.3 to 3.5 and 3.7 to
3.13 in Appendix M. For cooling mode and heating mode test
conditions, refer to section 6.2 of ANSI/AHRI Standard 1230-2010.
For calculations of seasonal performance descriptors use section 4
of Appendix M.
(B) For systems other than VRF, only a subset of the sections
listed in this test procedure apply when testing and rating a
particular unit. Table 1 shows the sections of the test procedure
that apply to each system. This table is meant to assist
manufacturers in finding the appropriate sections of the test
procedure; the appendix sections rather than the table provide the
specific requirements for testing, and given the varied nature of
available units, manufacturers are responsible for determining which
sections apply to each unit tested. To use this table, first refer
to the sections listed under ``all units''. Then refer to additional
requirements based on: (1) System configuration(s), (2) the
compressor staging or modulation capability, and (3) any special
features.
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Testing requirements for space-constrained products do not
differ from similar equipment that is not space-constrained and thus
are not listed separately in this table. Air conditioners and heat
pumps are not listed separately in this table, but heating
procedures and calculations apply only to heat pumps.
BILLING CODE 6450-01-P
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BILLING CODE 6450-01-C
* Does not apply to heating-only heat pumps.
** Applies only to heat pumps; not to air conditioners.
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[dagger] Use ANSI/AHRI Standard 1230-2010 with Addendum 2, with
the sections referenced in section 2(A) of this Appendix, in
conjunction with the sections set forth in the table to perform test
setup, testing, and calculations for rating VRF multiple-split and
VRF SDHV systems.
Note: For all units, use section 3.13 for off mode testing
procedures and section 4.3 for off mode calculations. For all units
subject to an EER standard, use section 4.7 to determine the energy
efficiency ratio.
2.1 Test room requirements.
a. Test using two side-by-side rooms, an indoor test room and an
outdoor test room. For multiple-split, single-zone-multi-coil or
multi-circuit air conditioners and heat pumps, however, use as many
available indoor test rooms as needed to accommodate the total
number of indoor units. These rooms must comply with the
requirements specified in sections 8.1.2 and 8.1.3 of ASHRAE
Standard 37-2009 (incorporated by reference, see Sec. 430.3).
b. Inside these test rooms, use artificial loads during cyclic
tests and Frost Accumulation tests, if needed, to produce stabilized
room air temperatures. For one room, select an electric resistance
heater(s) having a heating capacity that is approximately equal to
the heating capacity of the test unit's condenser. For the second
room, select a heater(s) having a capacity that is close to the
sensible cooling capacity of the test unit's evaporator. When
applied, cycle the heater located in the same room as the test unit
evaporator coil ON and OFF when the test unit cycles ON and OFF.
Cycle the heater located in the same room as the test unit
condensing coil ON and OFF when the test unit cycles OFF and ON.
2.2 Test unit installation requirements.
a. Install the unit according to section 8.2 of ASHRAE Standard
37-2009 (incorporated by reference, see Sec. 430.3), subject to the
following additional requirements:
(1) When testing split systems, follow the requirements given in
section 6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see
Sec. 430.3) with Addendum 1 and 2. For the vapor refrigerant
line(s), use the insulation included with the unit; if no insulation
is provided, refer to the specifications for the insulation in the
installation instructions included with the unit by the
manufacturer; if no insulation is included with the unit and the
installation instructions do not contain provisions for insulating
the line(s), fully insulate the vapor refrigerant line(s) with vapor
proof insulation having an inside diameter that matches the
refrigerant tubing and a nominal thickness of at least 0.5 inches.
For the liquid refrigerant line(s), use the insulation included with
the unit; if no insulation is provided, refer to the specifications
for the insulation in the installation instructions included with
the unit by the manufacturer; if no insulation is included with the
unit and the installation instructions do not contain provisions for
insulating the line(s), leave the liquid refrigerant line(s) exposed
to the air for air conditioners and heat pumps that heat and cool;
or, for heating-only heat pumps, insulate the liquid refrigerant
line(s) with insulation having an inside diameter that matches the
refrigerant tubing and a nominal thickness of at least 0.5 inches;
(2) When testing split systems, if the indoor unit does not ship
with a cooling mode expansion device, test the system using the
device as specified in the installation instructions provided with
the indoor unit. If none is specified, test the system using a
thermostatic expansion valve with internal pressure equalization
that the valve manufacturer's product literature indicates is
appropriate for the system.
(3) When testing triple-split systems (see section 1.2,
Definitions), use the tubing length specified in section 6.1.3.5 of
AHRI 210/240-2008 (incorporated by reference, see Sec. 430.3) with
Addendum 1 and 2 to connect the outdoor coil, indoor compressor
section, and indoor coil while still meeting the requirement of
exposing 10 feet of the tubing to outside conditions; or
(4) When testing split systems having multiple indoor coils,
connect each indoor blower-coil to the outdoor unit using: (a) 25
feet of tubing, or (b) tubing furnished by the manufacturer,
whichever is longer.
If they are needed to make a secondary measurement of capacity,
install refrigerant pressure measuring instruments as described in
section 8.2.5 of ASHRAE Standard 37-2009 (incorporated by reference,
see Sec. 430.3). Refer to section 2.10 of this appendix to learn
which secondary methods require refrigerant pressure measurements.
At a minimum, insulate the low-pressure line(s) of a split system
with insulation having an inside diameter that matches the
refrigerant tubing and a nominal thickness of 0.5 inch.
b. For units designed for both horizontal and vertical
installation or for both up-flow and down-flow vertical
installations, the manufacturer must use the orientation for testing
specified in the certification report. Conduct testing with the
following installed:
(1) The most restrictive filter(s);
(2) Supplementary heating coils; and
(3) Other equipment specified as part of the unit, including all
hardware used by a heat comfort controller if so equipped (see
section 1, Definitions). For small-duct, high-velocity systems,
configure all balance dampers or restrictor devices on or inside the
unit to fully open or lowest restriction.
c. Testing a ducted unit without having an indoor air filter
installed is permissible as long as the minimum external static
pressure requirement is adjusted as stated in Table 3, note 3 (see
section 3.1.4). Except as noted in section 3.1.10, prevent the
indoor air supplementary heating coils from operating during all
tests. For coil-only indoor units that are supplied without an
enclosure, create an enclosure using 1 inch fiberglass ductboard
having a nominal density of 6 pounds per cubic foot. Or
alternatively, use some other insulating material having a thermal
resistance (``R'' value) between 4 and 6 hr[middot]ft\2\[middot]
[deg]F/Btu. For units where the coil is housed within an enclosure
or cabinet, no extra insulating or sealing is allowed.
d. When testing coil-only central air conditioners and heat
pumps, install a toroidal-type transformer to power the system's
low-voltage components, complying with any additional requirements
for this transformer mentioned in the installation manuals included
with the unit by the manufacturer. If the installation manuals do
not provide specifications for the transformer, use a transformer
having the following features: (1) A nominal volt-amp rating that
results in the transformer being loaded at a level that is between
25 and 90 percent based on the highest power value expected and then
confirmed during the off mode test; (2) designed to operate with a
primary input of 230 V, single phase, 60 Hz; and (3) that provides
an output voltage that is within the specified range for each low-
voltage component. The power consumption of the components connected
to the transformer must be included as part of the total system
power consumption during the off mode tests, less if included the
power consumed by the transformer when no load is connected to it.
e. An outdoor unit with no match (i.e., that is not sold with
indoor units) shall be tested without an indoor blower installed,
with a single cooling air volume rate, using an indoor unit whose
coil has (1) round tubes of outer diameter no less than 0.375
inches, and (2) a normalized gross indoor fin surface (NGIFS) no
greater than 1.15 square inches per British thermal unit per hour
(sq. in./Btu/hr). NGIFS is calculated as follows:
NGIFS = 2 x Lf x Wf x Nf / Qc(95)
where,
Lf = Indoor coil fin length in inches, also height of the
coil transverse to the tubes.
Wf = Indoor coil fin width in inches, also depth of the
coil.
Nf = Number of fins.
Qc(95) = the measured space cooling capacity of the tested outdoor
unit/indoor unit combination as determined from the A2 or A Test
whichever applies, Btu/h.
2.2.1 Defrost control settings.
Set heat pump defrost controls at the normal settings which most
typify those encountered in generalized climatic region IV. (Refer
to Figure 1 and Table 19 of section 4.2 for information on region
IV.) For heat pumps that use a time-adaptive defrost control system
(see section 1.2, Definitions), the manufacturer must specify the
frosting interval to be used during Frost Accumulation tests and
provide the procedure for manually initiating the defrost at the
specified time. To ease testing of any unit, the manufacturer should
provide information and any necessary hardware to manually initiate
a defrost cycle.
2.2.2 Special requirements for units having a multiple-speed
outdoor fan.
Configure the multiple-speed outdoor fan according to the
installation manual included with the unit by the manufacturer, and
thereafter, leave it unchanged for all tests. The controls of the
unit must regulate the operation of the outdoor fan during all lab
tests except dry coil cooling mode tests. For dry coil cooling mode
tests, the outdoor fan must operate at the same speed used during
the required wet coil test conducted at the same outdoor test
conditions.
2.2.3 Special requirements for multi-split air conditioners and
heat pumps, systems composed of multiple single-zone-multiple-coil
split-system units (having multiple outdoor units located side-by-
side), and ducted systems using a single indoor section
[[Page 69350]]
containing multiple blowers that would normally operate using two or
more indoor thermostats.
Because these systems will have more than one indoor blower and
possibly multiple outdoor fans and compressor systems, references in
this test procedure to a singular indoor blower, outdoor fan, and
compressor means all indoor blowers, all outdoor fans, and all
compressor systems that are energized during the test.
a. Additional requirements for multi-split air conditioners and
heat pumps and systems composed of multiple single-zone-multiple-
coil split-system units. For any test where the system is operated
at part load (i.e., one or more compressors ``off'', operating at
the intermediate or minimum compressor speed, or at low compressor
capacity), the manufacturer shall designate the indoor coil(s) that
are not providing heating or cooling during the test such that the
sum of the nominal heating or cooling capacity of the operational
indoor units is within 5 percent of the intended part load heating
or cooling capacity. For variable-speed systems, the manufacturer
must designate at least one indoor unit that is not providing
heating or cooling for all tests conducted at minimum compressor
speed. For all other part-load tests, the manufacturer shall choose
to turn off zero, one, two, or more indoor units. The chosen
configuration shall remain unchanged for all tests conducted at the
same compressor speed/capacity. For any indoor coil that is not
providing heating or cooling during a test, cease forced airflow
through this indoor coil and block its outlet duct.
b. Additional requirements for ducted systems with a single
indoor section containing multiple blowers where the blowers are
designed to cycle on and off independently of one another and are
not controlled such that all blowers are modulated to always operate
at the same air volume rate or speed. This Appendix covers systems
with a single-speed compressor or systems offering two fixed stages
of compressor capacity (e.g., a two-speed compressor, two single-
speed compressors). For any test where the system is operated at its
lowest capacity--i.e., the lowest total air volume rate allowed when
operating the single-speed compressor or when operating at low
compressor capacity--blowers accounting for at least one-third of
the full-load air volume rate must be turned off unless prevented by
the controls of the unit. In such cases, turn off as many blowers as
permitted by the unit's controls. Where more than one option exists
for meeting this ``off'' blower requirement, the manufacturer shall
include in its installation manuals included with the unit which
blower(s) are turned off. The chosen configuration shall remain
unchanged for all tests conducted at the same lowest capacity
configuration. For any indoor coil turned off during a test, cease
forced airflow through any outlet duct connected to an ``off''
blower.
c. For test setups where it is physically impossible for the
laboratory to use the required line length listed in Table 3 of
ANSI/AHRI Standard 1230-2010 (incorporated by reference, see Sec.
430.3) with Addendum 2, then the actual refrigerant line length used
by the laboratory may exceed the required length and the refrigerant
line length correction factors in Table 4 of ANSI/AHRI Standard
1230-2010 with Addendum 2 are applied.
2.2.4 Wet-bulb temperature requirements for the air entering the
indoor and outdoor coils.
2.2.4.1 Cooling mode tests. For wet-coil cooling mode tests,
regulate the water vapor content of the air entering the indoor unit
to the applicable wet-bulb temperature listed in Tables 4 to 7. As
noted in these same tables, achieve a wet-bulb temperature during
dry-coil cooling mode tests that results in no condensate forming on
the indoor coil. Controlling the water vapor content of the air
entering the outdoor side of the unit is not required for cooling
mode tests except when testing:
(1) Units that reject condensate to the outdoor coil during wet
coil tests. Tables 4-7 list the applicable wet-bulb temperatures.
(2) Single-package units where all or part of the indoor section
is located in the outdoor test room. The average dew point
temperature of the air entering the outdoor coil during wet coil
tests must be within 3.0 [deg]F of the average dew point
temperature of the air entering the indoor coil over the 30-minute
data collection interval described in section 3.3. For dry coil
tests on such units, it may be necessary to limit the moisture
content of the air entering the outdoor side of the unit to meet the
requirements of section 3.4.
2.2.4.2 Heating mode tests.
For heating mode tests, regulate the water vapor content of the
air entering the outdoor unit to the applicable wet-bulb temperature
listed in Tables 11 to 14. The wet-bulb temperature entering the
indoor side of the heat pump must not exceed 60 [deg]F.
Additionally, if the Outdoor Air Enthalpy test method is used while
testing a single-package heat pump where all or part of the outdoor
section is located in the indoor test room, adjust the wet-bulb
temperature for the air entering the indoor side to yield an indoor-
side dew point temperature that is as close as reasonably possible
to the dew point temperature of the outdoor-side entering air.
2.2.5 Additional refrigerant charging requirements.
2.2.5.1 The ``manufacturer's published instructions,'' as stated
in section 8.2 of ASHRAE Standard 37-2009 (incorporated by
reference, see Sec. 430.3) and ``manufacturer's installation
instructions'' discussed in this Appendix mean the manufacturer's
installation instructions that come packaged with or appear in the
labels applied to the unit. This does not include online manuals.
Installation instructions that are shipped with the unit shall take
precedence over installation instructions that appear in the labels
applied to the unit.
2.2.5.2 Instructions to Use for Charging.
a. Where the manufacturer's installation instructions contain
two sets of refrigerant charging criteria, one for field
installations and one for lab testing, use the field installation
criteria.
b. For systems consisting of an outdoor unit manufacturer's
outdoor section and indoor section with differing charging
procedures the refrigerant charge shall be adjusted per the outdoor
installation instructions.
c. For systems consisting of an outdoor unit manufacturer's
outdoor section and an independent coil manufacturer's indoor
section with differing charging procedures the refrigerant charge
shall be adjusted per the indoor installation instructions.
2.2.5.3 Test(s) to Use for Charging.
a. Use the tests or operating conditions specified in the
manufacturer's installation instructions for charging.
b. If the manufacturer's installation instructions do not
specify a test or operating conditions for charging or there are no
manufacturer's instructions, use the following test(s):
(1) For air conditioners or cooling and heating heat pumps, use
the A or A2 test.
(2) For cooling and heating heat pumps that do not function in
the H1 or H12 test with the charge set for the A or
A2 test and for heating-only heat pumps, use the H1 or
H12 test.
2.2.5.4 Parameters to Set and Their Target Values.
a. Consult the manufacturer's installation instructions
regarding which parameters to set and their target values. If the
instructions provide ranges of values, select target values equal to
the midpoints of the provided ranges.
b. In the event of conflicting information between charging
instructions (defined as multiple conditions given for charge
adjustment where all conditions specified cannot be met), follow the
following hierarchy.
(1) For fixed orifice systems:
(i) Superheat
(ii) High side pressure or corresponding saturation or dew-point
temperature
(iii) Low side pressure or corresponding saturation or dew-point
temperature
(iv) Low side temperature
(iii) High side temperature
(iv) Charge weight
(2) For expansion valve systems:
(i) Subcooling
(ii) High side pressure or corresponding saturation or dew-point
temperature
(iii) Low side pressure or corresponding saturation or dew-point
temperature
(iv) Approach temperature (difference between temperature of
liquid leaving condenser and condenser average inlet air
temperature)
(v) Charge weight
c. If there are no installation instructions and/or they do not
provide parameters and target values, set superheat to a target
value of 12 [deg]F for fixed orifice systems or set subcooling to a
target value of 10 [deg]F for expansion valve systems.
2.2.5.5 Charging Tolerances.
a. If the manufacturer's installation instructions specify
tolerances on target values for the charging parameters, set the
values using these tolerances.
b. Otherwise, use the following tolerances for the different
charging parameters:
1. Superheat: +/-2.0 [deg]F
2. Subcooling: +/-0.6 [deg]F
[[Page 69351]]
3. High side pressure or corresponding saturation or dew point
temperature: +/-4.0 psi or +/-1.0 [deg]F
4. Low side pressure or corresponding saturation or dew point
temperature: +/-2.0 psi or +/-0.8 [deg]F
5. High side temperature: +/-2.0 [deg]F
6. Low side temperature: +/-2.0 [deg]F
7. Approach temperature: +/-1.0 [deg]F
8. Charge weight: +/-2.0 ounce
2.2.5.6 Special Charging Instructions.
a. Cooling and Heating Heat Pumps
If, using the initial charge set in the A or A2 test,
the conditions are not within the range specified in manufacturer's
instructions for the H1 or H12 test, make as small as
possible an adjustment to obtain conditions for this test in the
specified range. After this adjustment, recheck conditions in the A
or A2 test to confirm that they are still within the
specified range for this test.
b. Single-Package Systems
Unless otherwise directed by the manufacturer's installation
instructions, install one or more refrigerant line pressure gauges
during the setup of the unit if setting of refrigerant charge is
based on certain operating parameters:
(1) Install a pressure gauge on the liquid line if charging is
on the basis of subcooling, or high side pressure or corresponding
saturation or dew point temperature;
(2) Install a pressure gauge on the suction line if charging is
on the basis of superheat, or low side pressure or corresponding
saturation or dew point temperature. If manufacturer's installation
instructions indicate that pressure gauges are not to be installed,
setting of charge shall not be based on any of the parameters listed
in b.(1) and (2) of this section.
2.2.5.7 Near-azeotropic and zeotropic refrigerants.
Charging of near-azeotropic and zeotropic refrigerants shall
only be performed with refrigerant in the liquid state.
2.2.5.8 Adjustment of charge between tests.
After charging the system as described in this test procedure,
use the set refrigerant charge for all tests used to determine
performance. Do not adjust the refrigerant charge at any point
during testing.
2.3 Indoor air volume rates.
If a unit's controls allow for overspeeding the indoor blower
(usually on a temporary basis), take the necessary steps to prevent
overspeeding during all tests.
2.3.1 Cooling tests.
a. Set indoor blower airflow-control settings (e.g., fan motor
pin settings, fan motor speed) according to the installation
instructions that are provided with the equipment while meeting the
airflow requirements that are specified in section 3.1.4 of this
appendix. If the manufacturer installation instructions do not
provide guidance on the airflow-control settings for a system tested
with the indoor blower installed, select the lowest speed that will
satisfy the minimum external static pressure specified in section
3.1.4.1.1 of this appendix with an air volume rate at or higher than
the rated full-load cooling air volume rate while meeting the
maximum air flow requirement.
b. Express the Cooling Full-load Air Volume Rate, the Cooling
Minimum Air Volume Rate, and the Cooling Intermediate Air Volume
Rate in terms of standard air.
2.3.2 Heating tests.
a. If needed, set the indoor blower airflow-control settings
(e.g., fan motor pin settings, fan motor speed) according to the
installation instructions that are provided with the equipment. Do
this set-up while meeting all applicable airflow requirements
specified in sections 3.1.4 of this appendix. For a cooling and
heating heat pump tested with an indoor blower installed, if the
manufacturer installation instructions do not provide guidance on
the fan airflow-control settings, use the same airflow-control
settings used for the cooling test. If the manufacturer installation
instructions do not provide guidance on the airflow-control settings
for a heating-only heat pump tested with the indoor blower
installed, select the lowest speed that will satisfy the minimum
external static pressure specified in section 3.1.4.4.3 of this
appendix with an air volume rate at or higher than the rated heating
full-load air volume rate.
b. Express the Heating Full-Load Air Volume Rate, the Heating
Minimum Air Volume Rate, the Heating Intermediate Air Volume Rate,
and the Heating Nominal Air Volume Rate in terms of standard air.
2.4 Indoor coil inlet and outlet duct connections.
Insulate and/or construct the outlet plenum described in section
2.4.1 of this appendix and, if installed, the inlet plenum described
in section 2.4.2 of this appendix with thermal insulation having a
nominal overall resistance (R-value) of at least 19
hr[middot]ft\2\[middot] [deg]F/Btu.
2.4.1 Outlet plenum for the indoor unit.
a. Attach a plenum to the outlet of the indoor coil. (NOTE: for
some packaged systems, the indoor coil may be located in the outdoor
test room.)
b. For systems having multiple indoor coils, or multiple indoor
blowers within a single indoor section, attach a plenum to each
indoor coil or blower outlet. Connect two or more outlet plenums to
a single common duct so that each indoor coil ultimately connects to
an airflow measuring apparatus (section 2.6). If using more than one
indoor test room, do likewise, creating one or more common ducts
within each test room that contains multiple indoor coils. At the
plane where each plenum enters a common duct, install an adjustable
airflow damper and use it to equalize the static pressure in each
plenum. Each outlet air temperature grid (section 2.5.4) and airflow
measuring apparatus are located downstream of the inlet(s) to the
common duct.
c. For small-duct, high-velocity systems, install an outlet
plenum that has a diameter that is equal to or less than the value
listed below. The limit depends only on the Cooling Full-Load Air
Volume Rate (see section 3.1.4.1.1 of this appendix) and is
effective regardless of the flange dimensions on the outlet of the
unit (or an air supply plenum adapter accessory, if installed in
accordance with the manufacturer's installation instructions).
d. Add a static pressure tap to each face of the (each) outlet
plenum, if rectangular, or at four evenly distributed locations
along the circumference of an oval or round plenum. Create a
manifold that connects the four static pressure taps. Figures 7a,
7b, 7c of ASHRAE Standard 37-2009 (incorporated by reference, see
Sec. 430.3) shows two of the three options allowed for the manifold
configuration; the third option is the broken-ring, four-to-one
manifold configuration that is shown in Figure 7a of ASHRAE Standard
37-2009. See Figures 7a, 7b, 7c, and 8 of ASHRAE Standard 37-2009
for the cross-sectional dimensions and minimum length of the (each)
plenum and the locations for adding the static pressure taps for
units tested with and without an indoor blower installed.
Table 2--Size of Outlet Plenum
------------------------------------------------------------------------
Maximum diameter
Cooling full-load air volume rate (scfm) * of outlet
plenum (inches)
------------------------------------------------------------------------
<=500................................................. 6
501 to 700............................................ 7
701 to 900............................................ 8
901 to 1100........................................... 9
1101 to 1400.......................................... 10
1401 to 1750.......................................... 11
------------------------------------------------------------------------
* If the outlet plenum is rectangular, calculate its equivalent diameter
using (4A/P,) where A is the cross-sectional area and P is the
perimeter of the rectangular plenum, and compare it to the listed
maximum diameter.
2.4.2 Inlet plenum for the indoor unit.
Install an inlet plenum when testing a coil-only indoor unit or
a packaged system where the indoor coil is located in the outdoor
test room. Add static pressure taps at the center of each face of
this plenum, if rectangular, or at four evenly distributed locations
along the circumference of an oval or round plenum. Make a manifold
that connects the four static-pressure taps using one of the three
configurations specified in section 2.4.1. See Figures 7b, 7c, and
Figure 8 of ASHRAE Standard 37-2009 (incorporated by reference, see
Sec. 430.3) for cross-sectional dimensions, the minimum length of
the inlet plenum, and the locations of the static-pressure taps.
When testing a ducted unit having an indoor blower (and the indoor
coil is in the indoor test room), test with an inlet plenum
installed unless physically prohibited by space limitations within
the test room. If used, construct the inlet plenum and add the four
static-pressure taps as shown in Figure 8 of ASHRAE Standard 37-
2009. If used, the inlet duct size shall equal the size of the inlet
opening of the air-handling (blower coil) unit or furnace, with a
minimum length of 6 inches. Manifold the four static-pressure taps
using one of the three configurations specified in section 2.4.1.d.
Never use an inlet plenum when testing a non-ducted system.
2.5 Indoor coil air property measurements and air damper box
applications.
Follow instructions for indoor coil air property measurements as
described in AHRI 210/240-Draft, appendix E, section E4, unless
otherwise instructed in this section.
[[Page 69352]]
a. Measure the dry-bulb temperature and water vapor content of
the air entering and leaving the indoor coil. If needed, use an air
sampling device to divert air to a sensor(s) that measures the water
vapor content of the air. See Section 5.3 of ASHRAE Standard 41.1-
2013 (incorporated by reference, see Sec. 430.3) for guidance on
constructing an air sampling device. No part of the air sampling
device or the tubing transferring the sampled air to the sensor
shall be within two inches of the test chamber floor, and the
transfer tubing shall be insulated. The sampling device may also
divert air to a remotely located sensor(s) that measures dry bulb
temperature. The air sampling device and the remotely located
temperature sensor(s) may be used to determine the entering air dry
bulb temperature during any test. The air sampling device and the
remotely located leaving air dry bulb temperature sensor(s) may be
used for all tests except:
(1) Cyclic tests; and
(2) Frost accumulation tests.
b. An acceptable alternative in all cases, including the two
special cases noted above, is to install a grid of dry bulb
temperature sensors within the outlet and inlet ducts. Use a
temperature grid to get the average dry bulb temperature at one
location, leaving or entering, or when two grids are applied as a
thermopile, to directly obtain the temperature difference. A grid of
temperature sensors (which may also be used for determining average
leaving air dry bulb temperature) is required to measure the
temperature distribution within a cross-section of the leaving
airstream.
c. Use an inlet and outlet air damper box, an inlet upturned
duct, or any combination thereof when conducting one or both of the
cyclic tests listed in sections 3.2 and 3.6 on ducted systems.
Otherwise if not conducting one or both of said cyclic tests,
install an outlet air damper box when testing ducted and non-ducted
heat pumps that cycle off the indoor blower during defrost cycles if
no other means is available for preventing natural or forced
convection through the indoor unit when the indoor blower is off.
Never use an inlet damper box or an inlet upturned duct when testing
a non-ducted system. An inlet upturned duct is a length of ductwork
so installed upstream from the inlet such that the indoor duct inlet
opening, facing upwards, is sufficiently high to prevent natural
convection transfer out of the duct. If an inlet upturned duct is
used, install a dry bulb temperature sensor near the inlet opening
of the indoor duct at a centerline location not higher than the
lowest elevation of the duct edges at the inlet, and ensure that the
variation of the dry bulb temperature at this location, measured at
least every minute during the compressor OFF period of the cyclic
test, does not exceed 1.0 [deg]F.
2.5.1 Test set-up on the inlet side of the indoor coil: For
cases where the inlet airflow prevention device is installed.
a. Install an airflow prevention device as specified in section
2.5.1.1 or 2.5.1.2 of this appendix, whichever applies.
b. For an inlet damper box, locate the grid of entering air dry-
bulb temperature sensors, if used, and the air sampling device, or
the sensor used to measure the water vapor content of the inlet air,
at a location immediately upstream of the damper box inlet. For an
inlet upturned duct, locate the grid of entering air dry-bulb
temperature sensors, if used, and the air sampling device, or the
sensor used to measure the water vapor content of the inlet air, at
a location at least one foot downstream from the beginning of the
insulated portion of the duct but before the static pressure
measurement; install a dry-bulb temperature sensor at a centerline
location not higher than the lowest elevation of the duct edges at
the device inlet.
2.5.1.1 If the section 2.4.2 inlet plenum is installed.
Construct the airflow prevention device having a cross-sectional
flow area equal to or greater than the flow area of the inlet
plenum. Install the airflow prevention device upstream of the inlet
plenum and construct ductwork connecting it to the inlet plenum. If
needed, use an adaptor plate or a transition duct section to connect
the airflow prevention device with the inlet plenum. Insulate the
ductwork and inlet plenum with thermal insulation that has a nominal
overall resistance (R-value) of at least 19 hr [middot] ft\2\
[middot] [deg]F/Btu.
2.5.1.2 If the section 2.4.2 inlet plenum is not installed.
Construct the airflow prevention device having a cross-sectional
flow area equal to or greater than the flow area of the air inlet of
the indoor unit. Install the airflow prevention device immediately
upstream of the inlet of the indoor unit. If needed, use an adaptor
plate or a short transition duct section to connect the airflow
prevention device with the unit's air inlet. Add static pressure
taps at the center of each face of a rectangular airflow prevention
device, or at four evenly distributed locations along the
circumference of an oval or round airflow prevention device. Locate
the pressure taps between the airflow prevention device and the
inlet of the indoor unit. Make a manifold that connects the four
static pressure taps. Insulate the ductwork with thermal insulation
that has a nominal overall resistance (R-value) of at least 19 hr
[middot] ft\2\ [middot] [deg]F/Btu.
2.5.2 Test set-up on the inlet side of the indoor unit: For
cases where no airflow prevention device is installed.
If using the section 2.4.2 inlet plenum and a grid of dry bulb
temperature sensors, mount the grid at a location upstream of the
static pressure taps described in section 2.4.2, preferably at the
entrance plane of the inlet plenum. If the section 2.4.2 inlet
plenum is not used, but a grid of dry bulb temperature sensors is
used, locate the grid approximately 6 inches upstream from the inlet
of the indoor coil. Or, in the case of non-ducted units having
multiple indoor coils, locate a grid approximately 6 inches upstream
from the inlet of each indoor coil. Position an air sampling device,
or the sensor used to measure the water vapor content of the inlet
air, immediately upstream of the (each) entering air dry-bulb
temperature sensor grid. If a grid of sensors is not used, position
the entering air sampling device (or the sensor used to measure the
water vapor content of the inlet air) as if the grid were present.
2.5.3 Indoor coil static pressure difference measurement.
Section 6.5.2 of ASHRAE Standard 37-2009 (incorporated by
reference, see Sec. 430.3) describes the method for fabricating
static-pressure taps. Also refer to Figure 2A of ASHRAE Standard 51-
07/AMCA Standard 210-07 (incorporated by reference, see Sec.
430.3). Use a differential pressure measuring instrument that is
accurate to within 0.01 inches of water and has a
resolution of at least 0.01 inches of water to measure the static
pressure difference between the indoor coil air inlet and outlet.
Connect one side of the differential pressure instrument to the
manifolded pressure taps installed in the outlet plenum. Connect the
other side of the instrument to the manifolded pressure taps located
in either the inlet plenum or incorporated within the airflow
prevention device. If an inlet plenum or inlet airflow prevention
device is not used, leave the inlet side of the differential
pressure instrument open to the surrounding atmosphere. For non-
ducted systems that are tested with multiple outlet plenums, measure
the static pressure within each outlet plenum relative to the
surrounding atmosphere.
2.5.4 Test set-up on the outlet side of the indoor coil.
a. Install an interconnecting duct between the outlet plenum
described in section 2.4.1 of this appendix and the airflow
measuring apparatus described below in section 2.6. The cross-
sectional flow area of the interconnecting duct must be equal to or
greater than the flow area of the outlet plenum or the common duct
used when testing non-ducted units having multiple indoor coils. If
needed, use adaptor plates or transition duct sections to allow the
connections. To minimize leakage, tape joints within the
interconnecting duct (and the outlet plenum). Construct or insulate
the entire flow section with thermal insulation having a nominal
overall resistance (R-value) of at least 19 hr [middot] ft\2\
[middot] [deg]F/Btu.
b. Install a grid(s) of dry-bulb temperature sensors inside the
interconnecting duct. Also, install an air sampling device, or the
sensor(s) used to measure the water vapor content of the outlet air,
inside the interconnecting duct. Locate the dry-bulb temperature
grid(s) upstream of the air sampling device (or the in-duct
sensor(s) used to measure the water vapor content of the outlet
air). Air that circulates through an air sampling device and past a
remote water-vapor-content sensor(s) must be returned to the
interconnecting duct at a location:
(1) Downstream of the air sampling device;
(2) Upstream of the outlet air damper box, if installed; and
(3) Upstream of the section 2.6 airflow measuring apparatus.
2.5.4.1 Outlet air damper box placement and requirements.
If using an outlet air damper box (see section 2.5), install it
within the interconnecting duct at a location downstream of the
location where air from the sampling device is reintroduced or
downstream of the in-duct sensor that measures water vapor content
of the outlet air. The leakage rate from the combination of the
outlet plenum, the closed damper, and the duct section that connects
these two components must not exceed 20 cubic feet
[[Page 69353]]
per minute when a negative pressure of 1 inch of water column is
maintained at the plenum's inlet.
2.5.4.2 Procedures to minimize temperature maldistribution.
Use these procedures if necessary to correct temperature
maldistributions. Install a mixing device(s) upstream of the outlet
air, dry-bulb temperature grid (but downstream of the outlet plenum
static pressure taps). Use a perforated screen located between the
mixing device and the dry-bulb temperature grid, with a maximum open
area of 40 percent. One or both items should help to meet the
maximum outlet air temperature distribution specified in section
3.1.8. Mixing devices are described in sections 5.3.2 and 5.3.3 of
ASHRAE Standard 41.1-2013 and section 5.2.2 of ASHRAE Standard 41.2-
87 (RA 92) (incorporated by reference, see Sec. 430.3).
2.5.4.3 Minimizing air leakage.
For small-duct, high-velocity systems, install an air damper
near the end of the interconnecting duct, just prior to the
transition to the airflow measuring apparatus of section 2.6. To
minimize air leakage, adjust this damper such that the pressure in
the receiving chamber of the airflow measuring apparatus is no more
than 0.5 inch of water higher than the surrounding test room
ambient. If applicable, in lieu of installing a separate damper, use
the outlet air damper box of sections 2.5 and 2.5.4.1 of this
appendix if it allows variable positioning. Also apply these steps
to any conventional indoor blower unit that creates a static
pressure within the receiving chamber of the airflow measuring
apparatus that exceeds the test room ambient pressure by more than
0.5 inches of water column.
2.5.5 Dry bulb temperature measurement.
a. Measure dry bulb temperatures as specified in sections 4,
5.3, 6, 7.2, and 7.3 of ASHRAE Standard 41.1-2013 (incorporated by
reference, see Sec. 430.3).
b. Distribute the sensors of a dry-bulb temperature grid over
the entire flow area. The required minimum is 9 sensors per grid.
2.5.6 Water vapor content measurement.
Determine water vapor content by measuring dry-bulb temperature
combined with the air wet-bulb temperature, dew point temperature,
or relative humidity. If used, construct and apply wet-bulb
temperature sensors as specified in sections 4, 5, 6, 7.2, 7.3, 7.4,
and 7.5 of ASHRAE Standard 41.6-2014 (incorporated by reference, see
Sec. 430.3). The temperature sensor (wick removed) must be accurate
to within 0.2 [deg]F. If used, apply dew point
hygrometers as specified in sections 4, 5, 6, and 7.1 of ASHRAE
Standard 41.6-2014. The dew point hygrometers must be accurate to
within 0.4 [deg]F when operated at conditions that
result in the evaluation of dew points above 35 [deg]F. If used, a
relative humidity (RH) meter must be accurate to within 0.7% RH. Other means to determine the psychrometric state of
air may be used as long as the measurement accuracy is equivalent to
or better than the accuracy achieved from using a wet-bulb
temperature sensor that meets the above specifications.
2.5.7 Air damper box performance requirements.
If used (see section 2.5), the air damper box(es) must be
capable of being completely opened or completely closed within 10
seconds for each action.
2.6 Airflow measuring apparatus.
a. Fabricate and operate an Air Flow Measuring Apparatus as
specified in section 6.2 and 6.3 of ASHRAE Standard 37-2009
(incorporated by reference, see Sec. 430.3). Refer to Figure 12 of
ASHRAE Standard 51-07/AMCA Standard 210-07 or Figure 14 of ASHRAE
Standard 41.2-87 (RA 92) (incorporated by reference, see Sec.
430.3) for guidance on placing the static pressure taps and
positioning the diffusion baffle (settling means) relative to the
chamber inlet. When measuring the static pressure difference across
nozzles and/or velocity pressure at nozzle throats using electronic
pressure transducers and a data acquisition system, if high
frequency fluctuations cause measurement variations to exceed the
test tolerance limits specified in section 9.2 and Table 2 of ASHRAE
Standard 37-2009, dampen the measurement system such that the time
constant associated with response to a step change in measurement
(time for the response to change 63% of the way from the initial
output to the final output) is no longer than five seconds.
b. Connect the airflow measuring apparatus to the
interconnecting duct section described in section 2.5.4. See
sections 6.1.1, 6.1.2, and 6.1.4, and Figures 1, 2, and 4 of ASHRAE
Standard 37-2009; and Figures D1, D2, and D4 of AHRI 210/240-2008
(incorporated by reference, see Sec. 430.3) with Addendum 1 and 2
for illustrative examples of how the test apparatus may be applied
within a complete laboratory set-up. Instead of following one of
these examples, an alternative set-up may be used to handle the air
leaving the airflow measuring apparatus and to supply properly
conditioned air to the test unit's inlet. The alternative set-up,
however, must not interfere with the prescribed means for measuring
airflow rate, inlet and outlet air temperatures, inlet and outlet
water vapor contents, and external static pressures, nor create
abnormal conditions surrounding the test unit. (Note: Do not use an
enclosure as described in section 6.1.3 of ASHRAE Standard 37-2009
when testing triple-split units.)
2.7 Electrical voltage supply.
Perform all tests at the voltage specified in section 6.1.3.2 of
AHRI 210/240-2008 (incorporated by reference, see Sec. 430.3) with
Addendum 1 and 2 for ``Standard Rating Tests.'' If the voltage on
the nameplate of indoor and outdoor units differs, the voltage
supply on the outdoor unit shall be selected for testing. Measure
the supply voltage at the terminals on the test unit using a volt
meter that provides a reading that is accurate to within 1.0 percent of the measured quantity.
2.8 Electrical power and energy measurements.
a. Use an integrating power (watt-hour) measuring system to
determine the electrical energy or average electrical power supplied
to all components of the air conditioner or heat pump (including
auxiliary components such as controls, transformers, crankcase
heater, integral condensate pump on non-ducted indoor units, etc.).
The watt-hour measuring system must give readings that are accurate
to within 0.5 percent. For cyclic tests, this accuracy
is required during both the ON and OFF cycles. Use either two
different scales on the same watt-hour meter or two separate watt-
hour meters. Activate the scale or meter having the lower power
rating within 15 seconds after beginning an OFF cycle. Activate the
scale or meter having the higher power rating active within 15
seconds prior to beginning an ON cycle. For ducted units tested with
a fan installed, the ON cycle lasts from compressor ON to indoor
blower OFF. For ducted units tested without an indoor blower
installed, the ON cycle lasts from compressor ON to compressor OFF.
For non-ducted units, the ON cycle lasts from indoor blower ON to
indoor blower OFF. When testing air conditioners and heat pumps
having a variable-speed compressor, avoid using an induction watt/
watt-hour meter.
b. When performing section 3.5 and/or 3.8 cyclic tests on non-
ducted units, provide instrumentation to determine the average
electrical power consumption of the indoor blower motor to within
1.0 percent. If required according to sections 3.3, 3.4,
3.7, 3.9.1 of this appendix, and/or 3.10, of this appendix this same
instrumentation requirement applies when testing air conditioners
and heat pumps having a variable-speed constant-air-volume-rate
indoor blower or a variable-speed, variable-air-volume-rate indoor
blower.
2.9 Time measurements.
Make elapsed time measurements using an instrument that yields
readings accurate to within 0.2 percent.
2.10 Test apparatus for the secondary space conditioning
capacity measurement.
For all tests, use the Indoor Air Enthalpy Method to measure the
unit's capacity. This method uses the test set-up specified in
sections 2.4 to 2.6 of this appendix. In addition, for all steady-
state tests, conduct a second, independent measurement of capacity
as described in section 3.1.1. For split systems, use one of the
following secondary measurement methods: Outdoor Air Enthalpy
Method, Compressor Calibration Method, or Refrigerant Enthalpy
Method. For single-package units, use either the Outdoor Air
Enthalpy Method or the Compressor Calibration Method as the
secondary measurement.
2.10.1 Outdoor Air Enthalpy Method.
a. To make a secondary measurement of indoor space conditioning
capacity using the Outdoor Air Enthalpy Method, do the following:
(1) Measure the electrical power consumption of the test unit;
(2) Measure the air-side capacity at the outdoor coil; and
(3) Apply a heat balance on the refrigerant cycle.
b. The test apparatus required for the Outdoor Air Enthalpy
Method is a subset of the apparatus used for the Indoor Air Enthalpy
Method. Required apparatus includes the following:
(1) On the outlet side, an outlet plenum containing static
pressure taps (sections 2.4, 2.4.1, and 2.5.3),
(2) An airflow measuring apparatus (section 2.6),
(3) A duct section that connects these two components and itself
contains the
[[Page 69354]]
instrumentation for measuring the dry-bulb temperature and water
vapor content of the air leaving the outdoor coil (sections 2.5.4,
2.5.5, and 2.5.6), and
(4) On the inlet side, a sampling device and temperature grid
(section 2.11b.).
c. During the preliminary tests described in sections 3.11.1 and
3.11.1.1, measure the evaporator and condenser temperatures or
pressures. On both the outdoor coil and the indoor coil, solder a
thermocouple onto a return bend located at or near the midpoint of
each coil or at points not affected by vapor superheat or liquid
subcooling. Alternatively, if the test unit is not sensitive to the
refrigerant charge, install pressure gages to the access valves or
to ports created from tapping into the suction and discharge lines
according to sections 7.4.2 and 8.2.5 of ASHRAE Standard 37-2009.
Use this alternative approach when testing a unit charged with a
zeotropic refrigerant having a temperature glide in excess of
1[emsp14][deg]F at the specified test conditions.
2.10.2 Compressor Calibration Method.
Measure refrigerant pressures and temperatures to determine the
evaporator superheat and the enthalpy of the refrigerant that enters
and exits the indoor coil. Determine refrigerant flow rate or, when
the superheat of the refrigerant leaving the evaporator is less than
5[emsp14][deg]F, total capacity from separate calibration tests
conducted under identical operating conditions. When using this
method, install instrumentation, measure refrigerant properties, and
adjust the refrigerant charge according to section 7.4.2 and 8.2.5
of ASHRAE Standard 37-2009 (incorporated by reference, see Sec.
430.3). Use refrigerant temperature and pressure measuring
instruments that meet the specifications given in sections 5.1.1 and
5.2 of ASHRAE Standard 37-2009.
2.10.3 Refrigerant Enthalpy Method.
For this method, calculate space conditioning capacity by
determining the refrigerant enthalpy change for the indoor coil and
directly measuring the refrigerant flow rate. Use section 7.5.2 of
ASHRAE Standard 37-2009 (incorporated by reference, see Sec. 430.3)
for the requirements for this method, including the additional
instrumentation requirements, and information on placing the flow
meter and a sight glass. Use refrigerant temperature, pressure, and
flow measuring instruments that meet the specifications given in
sections 5.1.1, 5.2, and 5.5.1 of ASHRAE Standard 37-2009.
Refrigerant flow measurement device(s), if used, must be elevated at
least two feet from the test chamber floor or placed upon insulating
material having a total thermal resistance of at least R-12 and
extending at least one foot laterally beyond each side of the
device(s)' exposed surfaces, unless the device(s) are elevated at
least two feet from the floor.
2.11 Measurement of test room ambient conditions.
Follow instructions for measurement of test room ambient
conditions as described in AHRI 210/240-Draft, appendix E, section
E4, unless otherwise instructed in this section.
a. If using a test set-up where air is ducted directly from the
conditioning apparatus to the indoor coil inlet (see Figure 2, Loop
Air-Enthalpy Test Method Arrangement, of ASHRAE Standard 37-2009),
add instrumentation to permit measurement of the indoor test room
dry-bulb temperature.
b. For the outdoor side, install a grid of evenly-distributed
sensors on every air-permitting face on the inlet of the outdoor
unit, such that each measurement represents an air-inlet area of no
more than one square foot. This grid must be constructed and applied
as per section 5.3 of ASHRAE Standard 41.1-2013 (incorporated by
reference, see Sec. 430.3). The maximum and minimum temperatures
measured by these sensors may differ by no more than 1.5 [deg]F--
otherwise adjustments to the test room must be made to improve
temperature uniformity. The outdoor conditions shall be verified
with the air collected by air sampling device. Air collected by an
air sampling device at the air inlet of the outdoor unit for
transfer to sensors for measurement of temperature and/or humidity
shall be protected from temperature change as follows: Any surface
of the air conveying tubing in contact with surrounding air at a
different temperature than the sampled air shall be insulated with
thermal insulation with a nominal thermal resistance (R-value) of at
least 19 hr [middot]ft \2\ [middot] [deg]F/Btu, no part of the air
sampling device or the tubing conducting the sampled air to the
sensors shall be within two inches of the test chamber floor, and
pairs of measurements (e.g. dry bulb temperature and wet bulb
temperature) used to determine water vapor content of sampled air
shall be measured in the same location. Take steps (e.g., add or re-
position a lab circulating fan), as needed, to maximize temperature
uniformity within the outdoor test room. However, ensure that any
fan used for this purpose does not cause air velocities in the
vicinity of the test unit to exceed 500 feet per minute.
c. Measure dry bulb temperatures as specified in sections 4, 5,
7.2, 6, and 7.3 of ASHRAE Standard 41.1-2013. Measure water vapor
content as stated in section 2.5.6.
2.12 Measurement of indoor blower speed.
When required, measure fan speed using a revolution counter,
tachometer, or stroboscope that gives readings accurate to within
1.0 percent.
2.13 Measurement of barometric pressure.
Determine the average barometric pressure during each test. Use
an instrument that meets the requirements specified in section 5.2
of ASHRAE Standard 37-2009 (incorporated by reference, see Sec.
430.3).
3. Testing Procedures
3.1 General Requirements.
If, during the testing process, an equipment set-up adjustment
is made that would have altered the performance of the unit during
any already completed test, then repeat all tests affected by the
adjustment. For cyclic tests, instead of maintaining an air volume
rate, for each airflow nozzle, maintain the static pressure
difference or velocity pressure during an ON period at the same
pressure difference or velocity pressure as measured during the
steady-state test conducted at the same test conditions.
Use the testing procedures in this section to collect the data
used for calculating (1) performance metrics for central air
conditioners and heat pumps during the cooling season; (2)
performance metrics for heat pumps during the heating season; and
(3) power consumption metric(s) for central air conditioners and
heat pumps during the off mode season(s).
3.1.1 Primary and secondary test methods.
For all tests, use the Indoor Air Enthalpy Method test apparatus
to determine the unit's space conditioning capacity. The procedure
and data collected, however, differ slightly depending upon whether
the test is a steady-state test, a cyclic test, or a Frost
Accumulation test. The following sections described these
differences. For all steady-state tests (i.e., the A, A2,
A1, B, B2, B1, C, C1,
EV, F1, G1, H01, H1,
H12, H11, HIN, H3,
H32, and H31 Tests), in addition, use one of
the acceptable secondary methods specified in section 2.10 to
determine indoor space conditioning capacity. Calculate this
secondary check of capacity according to section 3.11. The two
capacity measurements must agree to within 6 percent to constitute a
valid test. For this capacity comparison, use the Indoor Air
Enthalpy Method capacity that is calculated in section 7.3 of ASHRAE
Standard 37-2009 (and, if testing a coil-only system, do not make
the after-test fan heat adjustments described in section 3.3, 3.4,
3.7, and 3.10 of this appendix). However, include the appropriate
section 3.3 to 3.5 and 3.7 to 3.10 fan heat adjustments within the
Indoor Air Enthalpy Method capacities used for the section 4
seasonal calculations.
3.1.2 Manufacturer-provided equipment overrides.
Where needed, the manufacturer must provide a means for
overriding the controls of the test unit so that the compressor(s)
operates at the specified speed or capacity and the indoor blower
operates at the specified speed or delivers the specified air volume
rate.
3.1.3 Airflow through the outdoor coil.
For all tests, meet the requirements given in section 6.1.3.4 of
AHRI 210/240-2008 (incorporated by reference, see Sec. 430.3) with
Addendum 1 and 2 when obtaining the airflow through the outdoor
coil.
3.1.3.1 Double-ducted. For products intended to be installed
with the outdoor airflow ducted, the unit shall be installed with
outdoor coil ductwork installed per manufacturer installation
instructions and shall operate between 0.10 and 0.15 in
H2O external static pressure. External static pressure
measurements shall be made in accordance with ASHRAE Standard 37-
2009 Section 6.4 and 6.5.
3.1.4 Airflow through the indoor coil.
Airflow setting(s) shall be determined before testing begins.
Unless otherwise specified within this or its subsections, no
changes shall be made to the airflow setting(s) after initiation of
testing.
3.1.4.1 Cooling Full-load Air Volume Rate.
3.1.4.1.1 Cooling Full-Load Air Volume Rate for Ducted Units.
The manufacturer must specify the cooling full-load air volume
rate and the instructions for setting fan speed or controls. Adjust
the cooling full-load air volume rate if needed to satisfy the
additional requirements of this
[[Page 69355]]
section. First, when conducting the A or A2 Test
(exclusively), the measured air volume rate, when divided by the
measured indoor air-side total cooling capacity must not exceed 37.5
cubic feet per minute of standard air (scfm) per 1000 Btu/h. If this
ratio is exceeded, reduce the air volume rate until this ratio is
equaled. Use this reduced air volume rate for all tests that call
for using the Cooling Full-load Air Volume Rate. Pressure
requirements are as follows:
a. For all ducted units tested with an indoor blower installed,
except those having a constant-air-volume-rate indoor blower:
1. Achieve the Cooling Full-load Air Volume Rate, determined in
accordance with the previous paragraph;
2. Measure the external static pressure;
3. If this pressure is equal to or greater than the applicable
minimum external static pressure cited in Table 3, the pressure
requirement is satisfied. Use the current air volume rate for all
tests that require the Cooling Full-load Air Volume Rate.
4. If the Table 3 minimum is not equaled or exceeded,
4a. reduce the air volume rate and increase the external static
pressure by adjusting the exhaust fan of the airflow measuring
apparatus until the applicable Table 3 minimum is equaled or
4b. until the measured air volume rate equals 90 percent of the
air volume rate from step 1, whichever occurs first.
5. If the conditions of step 4a occur first, the pressure
requirement is satisfied. Use the step 4a reduced air volume rate
for all tests that require the Cooling Full-load Air Volume Rate.
6. If the conditions of step 4b occur first, make an incremental
change to the set-up of the indoor blower (e.g., next highest fan
motor pin setting, next highest fan motor speed) and repeat the
evaluation process beginning at above step 1. If the indoor blower
set-up cannot be further changed, reduce the air volume rate and
increase the external static pressure by adjusting the exhaust fan
of the airflow measuring apparatus until the applicable Table 3
minimum is equaled. Use this reduced air volume rate for all tests
that require the Cooling Full-load Air Volume Rate.
b. For ducted units that are tested with a constant-air-volume-
rate indoor blower installed. For all tests that specify the Cooling
Full-load Air Volume Rate, obtain an external static pressure as
close to (but not less than) the applicable Table 3 value that does
not cause automatic shutdown of the indoor blower or air volume rate
variation QVar, defined as follows, greater than 10
percent.
[GRAPHIC] [TIFF OMITTED] TP09NO15.010
Where:
Qmax = maximum measured airflow value
Qmin = minimum measured airflow value
QVar = airflow variance, percent
Additional test steps as described in section 3.3.(e) of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For ducted units that are tested without an indoor fan
installed. For the A or A2 Test, (exclusively), the
pressure drop across the indoor coil assembly must not exceed 0.30
inches of water. If this pressure drop is exceeded, reduce the air
volume rate until the measured pressure drop equals the specified
maximum. Use this reduced air volume rate for all tests that require
the Cooling Full-load Air Volume Rate.
Table 3--Minimum External Static Pressure for Ducted Systems Tested With an Indoor Blower Installed
----------------------------------------------------------------------------------------------------------------
Minimum external resistance \3\ (inches of water)
--------------------------------------------------------
Rated cooling \1\ or heating \2\ capacity (Btu/h) Small-duct, high-
Short ducted velocity systems All other systems
systems \4\ 4 5
----------------------------------------------------------------------------------------------------------------
Up Thru 28,800......................................... 0.03 1.10 0.10
29,000 to 42,500....................................... 0.05 1.15 0.15
43,000 and Above....................................... 0.07 1.20 0.20
----------------------------------------------------------------------------------------------------------------
\1\ For air conditioners and heat pumps, the value cited by the manufacturer in published literature for the
unit's capacity when operated at the A or A2 Test conditions.
\2\ For heating-only heat pumps, the value the manufacturer cites in published literature for the unit's
capacity when operated at the H1 or H12 Test conditions.
\3\ For ducted units tested without an air filter installed, increase the applicable tabular value by 0.08
inches of water.
\4\ See section 1.2, Definitions, to determine if the equipment qualifies as a short-ducted or a small-duct,
high-velocity system.
\5\ If a closed-loop, air-enthalpy test apparatus is used on the indoor side, limit the resistance to airflow on
the inlet side of the indoor blower coil to a maximum value of 0.1 inch of water. Impose the balance of the
airflow resistance on the outlet side of the indoor blower.
d. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the full-load air volume rate with all
blowers operating unless prevented by the controls of the unit. In
such cases, turn on the maximum number of blowers permitted by the
unit's controls. Where more than one option exists for meeting this
``on'' blower requirement, which blower(s) are turned on must match
that specified by the manufacturer in the installation manuals
included with the unit. Conduct section 3.1.4.1.1 setup steps for
each blower separately. If two or more indoor blowers are connected
to a common duct as per section 2.4.1, either turn off the other
indoor blowers connected to the same common duct or temporarily
divert their air volume to the test room when confirming or
adjusting the setup configuration of individual blowers. If the
indoor blowers are all the same size or model, the target air volume
rate for each blower plenum equals the full-load air volume rate
divided by the number of ``on'' blowers. If different size blowers
are used within the indoor section, the allocation of the system's
full-load air volume rate assigned to each ``on'' blower must match
that specified by the manufacturer in the installation manuals
included with the unit.
3.1.4.1.2 Cooling Full-load Air Volume Rate for Non-ducted
Units.
For non-ducted units, the Cooling Full-load Air Volume Rate is
the air volume rate that results during each test when the unit is
operated at an external static pressure of zero inches of water.
3.1.4.2 Cooling Minimum Air Volume Rate.
The manufacturer must specify the cooling minimum air volume
rate and the instructions for setting fan speed or controls. The
target external static pressure, [Delta]Pst_i, for any
test ``i'' with a specified air volume rate not equal to the cooling
full-load air volume rate is determined as follows.
[GRAPHIC] [TIFF OMITTED] TP09NO15.011
Where:
[Delta]Pst_i = target minimum external static pressure
for test i;
[Delta]Pst_full = minimum external static pressure for
test A or A2 (Table 3);
Qi = air volume rate for test i; and
Qfull = cooling full-load air volume rate as measured
after setting and/or adjustment as described in section 3.1.4.1.1.
a. For ducted units tested with an indoor blower installed that
is not a constant-air-volume indoor blower, adjust for external
static pressure as follows.
1. Achieve the manufacturer-specified cooling minimum air volume
rate;
2. Measure the external static pressure;
3. If this pressure is equal to or greater than the target
minimum external static pressure calculated as described above, use
the
[[Page 69356]]
current air volume rate for all tests that require the cooling
minimum air volume rate.
4. If the target minimum is not equaled or exceeded,
4a. reduce the air volume rate and increase the external static
pressure by adjusting the exhaust fan of the airflow measuring
apparatus until the applicable target minimum is equaled or
4b. until the measured air volume rate equals 90 percent of the
air volume rate from step 1, whichever occurs first.
5. If the conditions of step 4a occur first, use the step 4a
reduced air volume rate for all tests that require the cooling
minimum air volume rate.
6. If the conditions of step 4b occur first, make an incremental
change to the set-up of the indoor fan (e.g., next highest fan motor
pin setting, next highest fan motor speed) and repeat the evaluation
process beginning at above step 1. If the indoor fan set-up cannot
be further changed, reduce the air volume rate and increase the
external static pressure by adjusting the exhaust fan of the airflow
measuring apparatus until the applicable target minimum is equaled.
Use this reduced air volume rate for all tests that require the
cooling minimum air volume rate.
b. For ducted units with constant-air-volume indoor blowers,
conduct all tests that specify the cooling minimum air volume rate--
(i.e., the A1, B1, C1,
F1, and G1 Tests)--at an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b, greater than 10 percent, while being as close
to, but not less than the target minimum external static pressure.
Additional test steps as described in section 3.3(e) of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For ducted two-capacity units that are tested without an
indoor blower installed, the Cooling Minimum Air Volume Rate is the
higher of (1) the rate specified by the installation instructions
included with the unit by the manufacturer or (2) 75 percent of the
Cooling Full-load Air Volume Rate. During the laboratory tests on a
coil-only (fanless) unit, obtain this Cooling Minimum Air Volume
Rate regardless of the pressure drop across the indoor coil
assembly.
d. For non-ducted units, the Cooling Minimum Air Volume Rate is
the air volume rate that results during each test when the unit
operates at an external static pressure of zero inches of water and
at the indoor fan setting used at low compressor capacity (two-
capacity system) or minimum compressor speed (variable-speed
system). For units having a single-speed compressor and a variable-
speed variable-air-volume-rate indoor fan, use the lowest fan
setting allowed for cooling.
e. For ducted systems having multiple indoor blowers within a
single indoor section, operate the indoor blowers such that the
lowest air volume rate allowed by the unit's controls is obtained
when operating the lone single-speed compressor or when operating at
low compressor capacity while meeting the requirements of section
2.2.3.2 for the minimum number of blowers that must be turned off.
Adjust for external static pressure and if necessary adjust air
volume rates as described in section 3.1.4.2.a if the indoor fan is
not a constant-air-volume indoor fan or as described in section
3.1.4.2.b if the indoor fan is a constant-air-volume indoor fan. The
sum of the individual ``on'' blowers' air volume rates is the
cooling minimum air volume rate for the system.
3.1.4.3 Cooling Intermediate Air Volume Rate.
The manufacturer must specify the cooling intermediate air
volume rate and the instructions for setting fan speed or controls.
Calculate target minimum external static pressure as described in
section 3.1.4.2.
a. For ducted units tested with an indoor blower, installed that
is not a constant-air-volume indoor blower, adjust for external
static pressure as described in section 3.1.4.2.a for cooling
minimum air volume rate.
b. For ducted units tested with constant-air-volume indoor
blowers installed, conduct the EV Test at an external
static pressure that does not cause an automatic shutdown of the
indoor blower or air volume rate variation QVar, defined
in section 3.1.4.1.1.b, greater than 10 percent, while being as
close to, but not less than the target minimum external static
pressure. Additional test steps as described in section 3.3(e) of
this appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For non-ducted units, the Cooling Intermediate Air Volume
Rate is the air volume rate that results when the unit operates at
an external static pressure of zero inches of water and at the fan
speed selected by the controls of the unit for the EV
Test conditions.
3.1.4.4 Heating Full-load Air Volume Rate.
3.1.4.4.1 Ducted heat pumps where the Heating and Cooling Full-
load Air Volume Rates are the same.
a. Use the Cooling Full-load Air Volume Rate as the Heating
Full-load Air Volume Rate for:
1. Ducted heat pumps tested with an indoor blower installed that
is not a constant-air-volume indoor blower that operates at the same
airflow-control setting during both the A (or A2) and the
H1 (or H12) Tests;
2. Ducted heat pumps tested with constant-air-flow indoor
blowers installed that provide the same air flow for the A (or
A2) and the H1 (or H12) Tests; and
3. Ducted heat pumps that are tested without an indoor blower
installed (except two-capacity northern heat pumps that are tested
only at low capacity cooling--see 3.1.4.4.2).
b. For heat pumps that meet the above criteria ``1'' and ``3,''
no minimum requirements apply to the measured external or internal,
respectively, static pressure. For heat pumps that meet the above
criterion ``2,'' test at an external static pressure that does not
cause an automatic shutdown of the indoor blower or air volume rate
variation QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but not less than, the
same Table 3 minimum external static pressure as was specified for
the A (or A2) cooling mode test. Additional test steps as
described in section 3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the target value by more
than 0.03 inches of water.
3.1.4.4.2 Ducted heat pumps where the Heating and Cooling Full-
load Air Volume Rates are different due to indoor blower operation.
The manufacturer must specify the heating full-load air volume
rate and the instructions for setting fan speed or controls.
Calculate target minimum external static pressure as described in
section 3.1.4.2.
a. For ducted heat pumps tested with an indoor blower installed
that is not a constant-air-volume indoor blower, adjust for external
static pressure as described in section 3.1.4.2.a for cooling
minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct all tests that specify the heating full-
load air volume rate at an external static pressure that does not
cause an automatic shutdown of the indoor blower or air volume rate
variation QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but not less than the
target minimum external static pressure. Additional test steps as
described in section 3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the target value by more
than 0.03 inches of water.
c. When testing ducted, two-capacity northern heat pumps (see
section 1.2, Definitions), use the appropriate approach of the above
two cases for units that are tested with an indoor blower installed.
For coil-only northern heat pumps, the Heating Full-load Air Volume
Rate is the lesser of the rate specified by the manufacturer in the
installation instructions included with the unit or 133 percent of
the Cooling Full-load Air Volume Rate. For this latter case, obtain
the Heating Full-load Air Volume Rate regardless of the pressure
drop across the indoor coil assembly.
d. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the heating full-load air volume rate
using the same ``on'' blowers as used for the cooling full-load air
volume rate. For systems where individual blowers regulate the speed
(as opposed to the cfm) of the indoor blower, use the first section
3.1.4.2 equation for each blower individually. Sum the individual
blower air volume rates to obtain the heating full-load air volume
rate for the system.
3.1.4.4.3 Ducted heating-only heat pumps.
The manufacturer must specify the Heating Full-load Air Volume
Rate.
a. For all ducted heating-only heat pumps tested with an indoor
blower installed, except those having a constant-air-volume-rate
indoor blower. Conduct the following steps only during the first
test, the H1 or H12 Test.
1. Achieve the Heating Full-load Air Volume Rate.
2. Measure the external static pressure.
3. If this pressure is equal to or greater than the Table 3
minimum external static pressure that applies given the heating-only
heat pump's rated heating capacity, use the
[[Page 69357]]
current air volume rate for all tests that require the Heating Full-
load Air Volume Rate.
4. If the Table 3 minimum is not equaled or exceeded,
4a. reduce the air volume rate and increase the external static
pressure by adjusting the exhaust fan of the airflow measuring
apparatus until the applicable Table 3 minimum is equaled or
4b. until the measured air volume rate equals 90 percent of the
manufacturer-specified Full-load Air Volume Rate, whichever occurs
first.
5. If the conditions of step 4a occurs first, use the step 4a
reduced air volume rate for all tests that require the Heating Full-
load Air Volume Rate.
6. If the conditions of step 4b occur first, make an incremental
change to the set-up of the indoor blower (e.g., next highest fan
motor pin setting, next highest fan motor speed) and repeat the
evaluation process beginning at above step 1. If the indoor blower
set-up cannot be further changed, reduce the air volume rate until
the applicable Table 3 minimum is equaled. Use this reduced air
volume rate for all tests that require the Heating Full-load Air
Volume Rate.
b. For ducted heating-only heat pumps that are tested with a
constant-air-volume-rate indoor blower installed. For all tests that
specify the Heating Full-load Air Volume Rate, obtain an external
static pressure that does not cause an automatic shutdown of the
indoor blower or air volume rate variation QVar, defined
in section 3.1.4.1.1.b, greater than 10 percent, while being as
close to, but not less than, the applicable Table 3 minimum.
Additional test steps as described in section 3.9.1(c) of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For ducted heating-only heat pumps that are tested without an
indoor blower installed. For the H1 or H12 Test,
(exclusively), the pressure drop across the indoor coil assembly
must not exceed 0.30 inches of water. If this pressure drop is
exceeded, reduce the air volume rate until the measured pressure
drop equals the specified maximum. Use this reduced air volume rate
for all tests that require the Heating Full-load Air Volume Rate.
3.1.4.4.4 Non-ducted heat pumps, including non-ducted heating-
only heat pumps.
For non-ducted heat pumps, the Heating Full-load Air Volume Rate
is the air volume rate that results during each test when the unit
operates at an external static pressure of zero inches of water.
3.1.4.5 Heating Minimum Air Volume Rate.
3.1.4.5.1 Ducted heat pumps where the Heating and Cooling
Minimum Air Volume Rates are the same.
a. Use the Cooling Minimum Air Volume Rate as the Heating
Minimum Air Volume Rate for:
1. Ducted heat pumps tested with an indoor blower installed that
is not a constant-air-volume indoor blower that operates at the same
airflow-control setting during both the A1 and the
H11 tests;
2. Ducted heat pumps tested with constant-air-flow indoor
blowers installed that provide the same air flow for the
A1 and the H11 Tests; and
3. Ducted heat pumps that are tested without an indoor blower
installed (except two-capacity northern heat pumps that are tested
only at low capacity cooling--see 3.1.4.4.2).
b. For heat pumps that meet the above criteria ``1'' and ``3,''
no minimum requirements apply to the measured external or internal,
respectively, static pressure. For heat pumps that meet the above
criterion ``2,'' test at an external static pressure that does not
cause an automatic shutdown of the indoor blower or air volume rate
variation QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but not less than, the
same target minimum external static pressure as was specified for
the A1 cooling mode test. Additional test steps as
described in section 3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the target value by more
than 0.03 inches of water.
3.1.4.5.2 Ducted heat pumps where the Heating and Cooling
Minimum Air Volume Rates are different due to indoor blower
operation.
The manufacturer must specify the heating minimum volume rate
and the instructions for setting fan speed or controls. Calculate
target minimum external static pressure as described in section
3.1.4.2.
a. For ducted heat pumps tested with an indoor blower installed
that is not a constant-air-volume indoor blower, adjust for external
static pressure as described in section 3.1.4.2.a for cooling
minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct all tests that specify the Heating
Minimum Air Volume Rate--(i.e., the H01, H11,
H21, and H31 Tests)--at an external static
pressure that does not cause an automatic shutdown of the indoor
blower while being as close to, but not less thanor air volume rate
variation QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but not less than the
target minimum external static pressure. Additional test steps as
described in section 3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the target value by more
than 0.03 inches of water.
c. For ducted two-capacity northern heat pumps that are tested
with an indoor blower installed, use the appropriate approach of the
above two cases.
d. For ducted two-capacity heat pumps that are tested without an
indoor blower installed, use the Cooling Minimum Air Volume Rate as
the Heating Minimum Air Volume Rate. For ducted two-capacity
northern heat pumps that are tested without an indoor blower
installed, use the Cooling Full-load Air Volume Rate as the Heating
Minimum Air Volume Rate. For ducted two-capacity heating-only heat
pumps that are tested without an indoor blower installed, the
Heating Minimum Air Volume Rate is the higher of the rate specified
by the manufacturer in the test setup instructions included with the
unit or 75 percent of the Heating Full-load Air Volume Rate. During
the laboratory tests on a coil-only system, obtain the Heating
Minimum Air Volume Rate without regard to the pressure drop across
the indoor coil assembly.
e. For non-ducted heat pumps, the Heating Minimum Air Volume
Rate is the air volume rate that results during each test when the
unit operates at an external static pressure of zero inches of water
and at the indoor blower setting used at low compressor capacity
(two-capacity system) or minimum compressor speed (variable-speed
system). For units having a single-speed compressor and a variable-
speed, variable-air-volume-rate indoor blower, use the lowest fan
setting allowed for heating.
f. For ducted systems with multiple indoor blowers within a
single indoor section, obtain the heating minimum air volume rate
using the same ``on'' blowers as used for the cooling minimum air
volume rate. For systems where individual blowers regulate the speed
(as opposed to the cfm) of the indoor blower, use the first section
3.1.4.5 equation for each blower individually. Sum the individual
blower air volume rates to obtain the heating minimum air volume
rate for the system.
3.1.4.6 Heating Intermediate Air Volume Rate.
The manufacturer must specify the heating intermediate air
volume rate and the instructions for setting fan speed or controls.
Calculate target minimum external static pressure as described in
section 3.1.4.2.
a. For ducted heat pumps tested with an indoor blower installed
that is not a constant-air-volume indoor blower, adjust for external
static pressure as described in section 3.1.4.2.a for cooling
minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct the H2V Test at an external
static pressure that does not cause an automatic shutdown of the
indoor blower or air volume rate variation QVar, defined
in section 3.1.4.1.1.b, greater than 10 percent, while being as
close to, but not less than the target minimum external static
pressure. Additional test steps as described in section 3.9.1(c) of
this appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For non-ducted heat pumps, the Heating Intermediate Air
Volume Rate is the air volume rate that results when the heat pump
operates at an external static pressure of zero inches of water and
at the fan speed selected by the controls of the unit for the
H2V Test conditions.
3.1.4.7 Heating Nominal Air Volume Rate.
The manufacturer must specify the heating nominal air volume
rate and the instructions for setting fan speed or controls.
Calculate target minimum external static pressure as described in
section 3.1.4.2. Make adjustments as described in section 3.14.6 for
heating intermediate air volume rate so that the target minimum
external static pressure is met or exceeded.
3.1.5 Indoor test room requirement when the air surrounding the
indoor unit is not
[[Page 69358]]
supplied from the same source as the air entering the indoor unit.
If using a test set-up where air is ducted directly from the air
reconditioning apparatus to the indoor coil inlet (see Figure 2,
Loop Air-Enthalpy Test Method Arrangement, of ASHRAE Standard 37-
2009), maintain the dry bulb temperature within the test room within
5.0[emsp14][deg]F of the applicable sections 3.2 and 3.6
dry bulb temperature test condition for the air entering the indoor
unit. Dew point shall be within 2[emsp14][deg]F of the required
inlet conditions.
3.1.6 Air volume rate calculations.
For all steady-state tests and for Frost Accumulation (H2,
H21, H22, H2V) tests, calculate the
air volume rate through the indoor coil as specified in sections
7.7.2.1 and 7.7.2.2 of ASHRAE Standard 37-2009 (incorporated by
reference, see Sec. 430.3). When using the Outdoor Air Enthalpy
Method, follow sections 7.7.2.1 and 7.7.2.2 to calculate the air
volume rate through the outdoor coil. To express air volume rates in
terms of standard air, use:
[GRAPHIC] [TIFF OMITTED] TP09NO15.012
Where,
Vis = air volume rate of standard (dry) air, (ft\3\/
min)da
Vimx = air volume rate of the air-water vapor mixture,
(ft\3\/min)mx
vn' = specific volume of air-water vapor mixture at the
nozzle, ft\3\ per lbm of the air-water vapor mixture
Wn = humidity ratio at the nozzle, lbm of water vapor per
lbm of dry air
0.075 = the density associated with standard (dry) air, (lbm/ft\3\)
vn = specific volume of the dry air portion of the
mixture evaluated at the dry-bulb temperature, vapor content, and
barometric pressure existing at the nozzle, ft\3\ per lbm of dry
air.
(Note: In the first printing of ASHRAE Standard 37-2009, the
second IP equation for Qmi should read,
[GRAPHIC] [TIFF OMITTED] TP09NO15.013
3.1.7 Test sequence.
Manufacturers may optionally operate the equipment under test
for a ``break-in'' period, not to exceed 20 hours, prior to
conducting the test method specified in this section. A manufacturer
who elects to use this optional compressor break-in period in its
certification testing should record this information (including the
duration) in the test data underlying the certified ratings that are
required to be maintained under 10 CFR 429.71. When testing a ducted
unit (except if a heating-only heat pump), conduct the A or
A2 Test first to establish the Cooling Full-load Air
Volume Rate. For ducted heat pumps where the Heating and Cooling
Full-load Air Volume Rates are different, make the first heating
mode test one that requires the Heating Full-load Air Volume Rate.
For ducted heating-only heat pumps, conduct the H1 or H12
Test first to establish the Heating Full-load Air Volume Rate. When
conducting an cyclic test, always conduct it immediately after the
steady-state test that requires the same test conditions. For
variable-speed systems, the first test using the Cooling Minimum Air
Volume Rate should precede the EV Test, and the first
test using the Heating Minimum Air Volume Rate must precede the
H2V Test. The test laboratory makes all other decisions
on the test sequence.
3.1.8 Requirement for the air temperature distribution leaving
the indoor coil.
For at least the first cooling mode test and the first heating
mode test, monitor the temperature distribution of the air leaving
the indoor coil using the grid of individual sensors described in
sections 2.5 and 2.5.4. For the 30-minute data collection interval
used to determine capacity, the maximum spread among the outlet dry
bulb temperatures from any data sampling must not exceed
1.5[emsp14][deg]F. Install the mixing devices described in section
2.5.4.2 to minimize the temperature spread.
3.1.9 Requirement for the air temperature distribution entering
the outdoor coil.
Monitor the temperatures of the air entering the outdoor coil
using the grid of temperature sensors described in section 2.11. For
the 30-minute data collection interval used to determine capacity,
the maximum difference between dry bulb temperatures measured at any
of these locations must not exceed 1.5[emsp14][deg]F.
3.1.10 Control of auxiliary resistive heating elements.
Except as noted, disable heat pump resistance elements used for
heating indoor air at all times, including during defrost cycles and
if they are normally regulated by a heat comfort controller. For
heat pumps equipped with a heat comfort controller, enable the heat
pump resistance elements only during the below-described, short
test. For single-speed heat pumps covered under section 3.6.1, the
short test follows the H1 or, if conducted, the H1C Test. For two-
capacity heat pumps and heat pumps covered under section 3.6.2, the
short test follows the H12 Test. Set the heat comfort
controller to provide the maximum supply air temperature. With the
heat pump operating and while maintaining the Heating Full-load Air
Volume Rate, measure the temperature of the air leaving the indoor-
side beginning 5 minutes after activating the heat comfort
controller. Sample the outlet dry-bulb temperature at regular
intervals that span 5 minutes or less. Collect data for 10 minutes,
obtaining at least 3 samples. Calculate the average outlet
temperature over the 10-minute interval, TCC.
3.2 Cooling mode tests for different types of air conditioners
and heat pumps.
3.2.1 Tests for a unit having a single-speed compressor, or a
multi-circuit system, that is tested with a fixed-speed indoor
blower installed, with a constant-air-volume-rate indoor blower
installed, or with no indoor blower installed.
Conduct two steady-state wet coil tests, the A and B Tests. Use
the two dry-coil tests, the steady-state C Test and the cyclic D
Test, to determine the cooling mode cyclic degradation coefficient,
CD\c\. If testing outdoor units of central air
conditioners or heat pumps that are not sold with indoor units,
assign CD\c\ the default value of 0.2. Table 4 specifies
test conditions for these four tests.
Table 4--Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Blower, a Constant Air Volume Rate Indoor
Blower, or No Indoor Blower
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A Test--required (steady, wet coil)... 80 67 95 \1\75 Cooling full-load.\2\
B Test--required (steady, wet coil)... 80 67 82 \1\65 Cooling full-load.\2\
C Test--required (steady, dry coil)... 80 (\3\) 82 .............. Cooling full-load.\2\
D Test--required (cyclic, dry coil)... 80 (\3\) 82 .............. (\4\)
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb
temperature of 57 [deg]F or less be used.)
[[Page 69359]]
\4\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C Test.
3.2.2 Tests for a unit having a single-speed compressor where
the indoor section uses a single variable-speed variable-air-volume
rate indoor blower or multiple blowers.
3.2.2.1 Indoor blower capacity modulation that correlates with
the outdoor dry bulb temperature or systems with a single indoor
coil but multiple blowers.
Conduct four steady-state wet coil tests: The A2,
A1, B2, and B1 Tests. Use the two
dry-coil tests, the steady-state C1 Test and the d
D1 Test, to determine the cooling mode cyclic degradation
coefficient, CD\c\.
3.2.2.2 Indoor blower capacity modulation based on adjusting the
sensible to total (S/T) cooling capacity ratio.
The testing requirements are the same as specified in section
3.2.1 and Table 4. Use a Cooling Full-load Air Volume Rate that
represents a normal installation. If performed, conduct the steady-
state C Test and the cyclic D Test with the unit operating in the
same S/T capacity control mode as used for the B Test.
Table 5--Cooling Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.2.2.1 Indoor Unit Requirements
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet coil).. 80 67 95 \1\ 75 Cooling full-load.\2\
A1 Test--required (steady, wet coil).. 80 67 95 \1\ 75 Cooling minimum.\3\
B2 Test--required (steady, wet coil).. 80 67 82 \1\ 65 Cooling full-load.\2\
B1 Test--required (steady, wet coil).. 80 67 82 \1\ 65 Cooling minimum.\3\
C1 Test \4\--required (steady, dry 80 (\4\) 82 .............. Cooling minimum.\3\
coil).
D1 Test \4\--required (cyclic, dry 80 (\4\) 82 (\5\)
coil).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ Defined in section 3.1.4.2.
\4\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb
temperature of 57 [deg]F or less be used.)
\5\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C1 Test.
3.2.3 Tests for a unit having a two-capacity compressor. (see
section 1.2, Definitions)
a. Conduct four steady-state wet coil tests: The A2,
B2, B1, and F1 Tests. Use the two
dry-coil tests, the steady-state C1 Test and the cyclic
D1 Test, to determine the cooling-mode cyclic-degradation
coefficient, CD\c\. Table 6 specifies test conditions for
these six tests.
b. For units having a variable speed indoor blower that is
modulated to adjust the sensible to total (S/T) cooling capacity
ratio, use Cooling Full-load and Cooling Minimum Air Volume Rates
that represent a normal installation. Additionally, if conducting
the dry-coil tests, operate the unit in the same S/T capacity
control mode as used for the B1 Test.
c. Test two-capacity, northern heat pumps (see section 1.2,
Definitions) in the same way as a single speed heat pump with the
unit operating exclusively at low compressor capacity (see section
3.2.1 and Table 4).
d. If a two-capacity air conditioner or heat pump locks out low-
capacity operation at higher outdoor temperatures, then use the two
dry-coil tests, the steady-state C2 Test and the cyclic
D2 Test, to determine the cooling-mode cyclic-degradation
coefficient that only applies to on/off cycling from high capacity,
CD\c\(k=2). The default CD\c\(k=2) is the same
value as determined or assigned for the low-capacity cyclic-
degradation coefficient, CD\c\ [or equivalently,
CD\c\(k=1)].
Table 6--Cooling Mode Test Conditions for Units Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit temperature
temperature ([deg]F) ([deg]F) Cooling air volume
Test description --------------------------------------------------------------------------- Compressor capacity rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet 80 67 95 \1\ 75................... High................ Cooling Full-
coil). Load.\2\
B2 Test--required (steady, wet 80 67 82 \1\ 65................... High................ Cooling Full-Load.
coil). \2\
B1 Test--required (steady, wet 80 67 82 \1\ 65................... Low................. Cooling Minimum. \3\
coil).
C2 Test--required (steady, dry- 80 (\4\) 82 High..................... Cooling Full-Load\2\ ....................
coil).
D2 Test--required (cyclic, dry- 80 (\4\) 82 High..................... (\5\)............... ....................
coil).
C1 Test--required (steady, dry- 80 (\4\) 82 Low...................... Cooling Minimum\3\.. ....................
coil).
D1 Test--required (cyclic, dry- 80 (\4\) 82 Low...................... (\6\)............... ....................
coil).
F1 Test--required (steady, wet 80 67 67 \1\53.5.................. Low................. Cooling Minimum.\3\
coil).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ Defined in section 3.1.4.2.
\4\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet-bulb
temperature of 57[emsp14][deg]F or less.
[[Page 69360]]
\5\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the C2 Test.
\6\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the C1 Test.
3.2.4 Tests for a unit having a variable-speed compressor.
a. Conduct five steady-state wet coil tests: The A2,
EV, B2, B1, and F1
Tests. Use the two dry-coil tests, the steady-state G1
Test and the cyclic I1 Test, to determine the cooling
mode cyclic degradation coefficient, CD\c\. Table 7
specifies test conditions for these seven tests. Determine the
intermediate compressor speed cited in Table 7 using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.014
where a tolerance of plus 5 percent or the next higher inverter
frequency step from that calculated is allowed.
b. For units that modulate the indoor blower speed to adjust the
sensible to total (S/T) cooling capacity ratio, use Cooling Full-
load, Cooling Intermediate, and Cooling Minimum Air Volume Rates
that represent a normal installation. Additionally, if conducting
the dry-coil tests, operate the unit in the same S/T capacity
control mode as used for the F1 Test.
c. For multiple-split air conditioners and heat pumps (except
where noted), the following procedures supersede the above
requirements: For all Table 7 tests specified for a minimum
compressor speed, at least one indoor unit must be turned off. The
manufacturer shall designate the particular indoor unit(s) that is
turned off. The manufacturer must also specify the compressor speed
used for the Table 7 EV Test, a cooling-mode intermediate
compressor speed that falls within \1/4\ and \3/4\ of the difference
between the maximum and minimum cooling-mode speeds. The
manufacturer should prescribe an intermediate speed that is expected
to yield the highest EER for the given EV Test conditions
and bracketed compressor speed range. The manufacturer can designate
that one or more indoor units are turned off for the EV
Test.
Table 7--Cooling Mode Test Condition for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit temperature
temperature ([deg]F) ([deg]F) Cooling air volume
Test description --------------------------------------------------------------------------- Compressor speed rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet 80 67 95 \1\ 75................... Maximum............. Cooling Full-
coil). Load.\2\
B2 Test--required (steady, wet 80 67 82 \1\ 65................... Maximum............. Cooling Full-
coil). Load.\2\
EV Test--required (steady, wet 80 67 87 \1\ 69................... Intermediate........ Cooling
coil). Intermediate.\3\
B1 Test--required (steady, wet 80 67 82 \1\ 65................... Minimum............. Cooling Minimum.\4\
coil).
F1 Test--required (steady, wet 80 67 67 \1\ 53.5................. Minimum............. Cooling Minimum.\4\
coil).
G1 Test \5\--required (steady, 80 (\6\) 67 Minimum.................. Cooling Minimum \4\.
dry-coil).
I1 Test \5\--required (cyclic, 80 (\6\) 67 Minimum.................. (\6\)...............
dry-coil).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ Defined in section 3.1.4.3.
\4\ Defined in section 3.1.4.2.
\5\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet bulb
temperature of 57 [deg]F or less.
\6\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the G1 Test.
3.2.5 Cooling mode tests for northern heat pumps with triple-
capacity compressors.
Test triple-capacity, northern heat pumps for the cooling mode
in the same way as specified in section 3.2.3 for units having a
two-capacity compressor.
3.2.6 Tests for an air conditioner or heat pump having a single
indoor unit having multiple blowers and offering two stages of
compressor modulation.
Conduct the cooling mode tests specified in section 3.2.3.
3.3 Test procedures for steady-state wet coil cooling mode tests
(the A, A2, A1, B, B2,
B1, EV, and F1 Tests).
a. For the pretest interval, operate the test room
reconditioning apparatus and the unit to be tested until maintaining
equilibrium conditions for at least 30 minutes at the specified
section 3.2 test conditions. Use the exhaust fan of the airflow
measuring apparatus and, if installed, the indoor blower of the test
unit to obtain and then maintain the indoor air volume rate and/or
external static pressure specified for the particular test.
Continuously record (see section 1.2, Definitions):
(1) The dry-bulb temperature of the air entering the indoor
coil,
(2) The water vapor content of the air entering the indoor coil,
(3) The dry-bulb temperature of the air entering the outdoor
coil, and
(4) For the section 2.2.4 cases where its control is required,
the water vapor content of the air entering the outdoor coil.
Refer to section 3.11 for additional requirements that depend on
the selected secondary test method.
b. After satisfying the pretest equilibrium requirements, make
the measurements specified in Table 3 of ASHRAE Standard 37-2009 for
the Indoor Air Enthalpy method and the user-selected secondary
method. Make said Table 3 measurements at equal intervals that span
5 minutes or less. Continue data sampling until reaching a 30-minute
period (e.g., four consecutive 10-minute samples) where the test
tolerances specified in Table 8 are satisfied. For those
[[Page 69361]]
continuously recorded parameters, use the entire data set from the
30-minute interval to evaluate Table 8 compliance. Determine the
average electrical power consumption of the air conditioner or heat
pump over the same 30-minute interval.
c. Calculate indoor-side total cooling capacity and sensible
cooling capacity as specified in sections 7.3.3.1 and 7.3.3.3 of
ASHRAE Standard 37-2009 (incorporated by reference, see Sec.
430.3). Do not adjust the parameters used in calculating capacity
for the permitted variations in test conditions. Evaluate air
enthalpies based on the measured barometric pressure. Use the values
of the specific heat of air given in section 7.3.3.1 for calculation
of the sensible cooling capacities. Assign the average total space
cooling capacity, average sensible cooling capacity, and electrical
power consumption over the 30-minute data collection interval to the
variables Qc\k\(T), Qsc\k\(T) and
[Edot]c\k\(T), respectively. For these three variables,
replace the ``T'' with the nominal outdoor temperature at which the
test was conducted. The superscript k is used only when testing
multi-capacity units. Use the superscript k=2 to denote a test with
the unit operating at high capacity or maximum speed, k=1 to denote
low capacity or minimum speed, and k=v to denote the intermediate
speed.
d. For units tested without an indoor blower installed, decrease
Qc\k\(T) by
[GRAPHIC] [TIFF OMITTED] TP09NO15.015
where Vs is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
Table 8--Test Operating and Test Condition Tolerances for Section 3.3
Steady-State Wet Coil Cooling Mode Tests and Section 3.4 Dry Coil
Cooling Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor dry-bulb, [deg]F................. .............. ..............
Entering temperature................ 2.0 0.5
Leaving temperature................. 2.0 ..............
Indoor wet-bulb, [deg]F................. .............. ..............
Entering temperature................ 1.0 \2\ 0.3
Leaving temperature................. \2\ 1.0 ..............
Outdoor dry-bulb, [deg]F................ .............. ..............
Entering temperature................ 2.0 0.5
Leaving temperature................. \3\ 2.0 ..............
Outdoor wet-bulb, [deg]F................ .............. ..............
Entering temperature................ 1.0 \4\ 0.3
Leaving temperature................. \3\ 1.0 ..............
External resistance to airflow, inches 0.12 \5\ 0.02
of water...............................
Electrical voltage, % of rdg............ 2.0 1.5
Nozzle pressure drop, % of rdg.......... 8.0 ..............
------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Only applies during wet coil tests; does not apply during steady-
state, dry coil cooling mode tests.
\3\ Only applies when using the Outdoor Air Enthalpy Method.
\4\ Only applies during wet coil cooling mode tests where the unit
rejects condensate to the outdoor coil.
\5\ Only applies when testing non-ducted units.
e. For air conditioners and heat pumps having a constant-air-
volume-rate indoor blower, the five additional steps listed below
are required if the average of the measured external static
pressures exceeds the applicable sections 3.1.4 minimum (or target)
external static pressure ([Delta]Pmin) by 0.03 inches of
water or more.
1. Measure the average power consumption of the indoor blower
motor ([Edot]fan,1) and record the corresponding external
static pressure ([Delta]P1) during or immediately
following the 30-minute interval used for determining capacity.
2. After completing the 30-minute interval and while maintaining
the same test conditions, adjust the exhaust fan of the airflow
measuring apparatus until the external static pressure increases to
approximately [Delta]P1 + ([Delta]P1 -
[Delta]Pmin).
3. After re-establishing steady readings of the fan motor power
and external static pressure, determine average values for the
indoor blower power ([Edot]fan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
4. Approximate the average power consumption of the indoor
blower motor at [Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TP09NO15.016
5. Increase the total space cooling capacity,
Qc\k\(T), by the quantity ([Edot]fan,1 -
[Edot]fan,min), when expressed on a Btu/h basis. Decrease
the total electrical power, [Edot]c\k\(T), by the same
fan power difference, now expressed in watts.
3.4 Test procedures for the steady-state dry-coil cooling-mode
tests (the C, C1, C2, and G1
Tests).
a. Except for the modifications noted in this section, conduct
the steady-state dry coil cooling mode tests as specified in section
3.3 for wet coil tests. Prior to recording data during the steady-
state dry coil test, operate the unit at least one hour after
achieving dry coil conditions. Drain the drain pan and plug the
drain opening. Thereafter, the drain pan should remain completely
dry.
b. Denote the resulting total space cooling capacity and
electrical power derived from the test as Qss,dry and
[Edot]ss,dry.With regard to a section 3.3 deviation, do
not adjust Qss,dry for duct losses (i.e., do not apply
section 7.3.3.3 of ASHRAE Standard 37-2009). In preparing for the
section 3.5 cyclic tests, record the average indoor-side air volume
rate, V, specific heat of the air, Cp,a (expressed on dry air
basis), specific volume of the air at the nozzles, v'n,
humidity ratio at the nozzles, Wn, and either pressure
difference or velocity pressure for the flow nozzles. For units
having a variable-speed indoor fan (that provides either a constant
or variable air volume rate) that will or may be tested during the
cyclic dry coil cooling mode test with the indoor fan turned off
(see section
[[Page 69362]]
3.5), include the electrical power used by the indoor fan motor
among the recorded parameters from the 30-minute test.
c. If the temperature sensors used to provide the primary
measurement of the indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the subsequent cyclic dry-
coil test are different, include measurements of the latter sensors
among the regularly sampled data. Beginning at the start of the 30-
minute data collection period, measure and compute the indoor-side
air dry-bulb temperature difference using both sets of
instrumentation, [Delta]T (Set SS) and [Delta]T (Set CYC), for each
equally spaced data sample. If using a consistent data sampling rate
that is less than 1 minute, calculate and record minutely averages
for the two temperature differences. If using a consistent sampling
rate of one minute or more, calculate and record the two temperature
differences from each data sample. After having recorded the seventh
(i=7) set of temperature differences, calculate the following ratio
using the first seven sets of values:
[GRAPHIC] [TIFF OMITTED] TP09NO15.017
Each time a subsequent set of temperature differences is
recorded (if sampling more frequently than every 5 minutes),
calculate FCD using the most recent seven sets of values.
Continue these calculations until the 30-minute period is completed
or until a value for FCD is calculated that falls outside
the allowable range of 0.94-1.06. If the latter occurs, immediately
suspend the test and identify the cause for the disparity in the two
temperature difference measurements. Recalibration of one or both
sets of instrumentation may be required. If all the values for
FCD are within the allowable range, save the final value
of the ratio from the 30-minute test as FCD*. If the
temperature sensors used to provide the primary measurement of the
indoor-side dry bulb temperature difference during the steady-state
dry-coil test and the subsequent cyclic dry-coil test are the same,
set FCD*= 1.
3.5 Test procedures for the cyclic dry-coil cooling-mode tests
(the D, D1, D2, and I1 Tests).
a. After completing the steady-state dry-coil test, remove the
Outdoor Air Enthalpy method test apparatus, if connected, and begin
manual OFF/ON cycling of the unit's compressor. The test set-up
should otherwise be identical to the set-up used during the steady-
state dry coil test. When testing heat pumps, leave the reversing
valve during the compressor OFF cycles in the same position as used
for the compressor ON cycles, unless automatically changed by the
controls of the unit. For units having a variable-speed indoor
blower, the manufacturer has the option of electing at the outset
whether to conduct the cyclic test with the indoor blower enabled or
disabled. Always revert to testing with the indoor blower disabled
if cyclic testing with the fan enabled is unsuccessful.
b. For units having a single-speed or two-capacity compressor,
cycle the compressor OFF for 24 minutes and then ON for 6 minutes
([Delta][tau]cyc,dry = 0.5 hours). For units having a
variable-speed compressor, cycle the compressor OFF for 48 minutes
and then ON for 12 minutes ([Delta][tau]cyc,dry = 1.0
hours). Repeat the OFF/ON compressor cycling pattern until the test
is completed. Allow the controls of the unit to regulate cycling of
the outdoor fan. If an upturned duct is used, measure the dry-bulb
temperature at the inlet of the device at least once every minute
and ensure that its test operating tolerance is within
1.0[emsp14][deg]F for each compressor OFF period.
c. Sections 3.5.1 and 3.5.2 specify airflow requirements through
the indoor coil of ducted and non-ducted systems, respectively. In
all cases, use the exhaust fan of the airflow measuring apparatus
(covered under section 2.6) along with the indoor blower of the
unit, if installed and operating, to approximate a step response in
the indoor coil airflow. Regulate the exhaust fan to quickly obtain
and then maintain the flow nozzle static pressure difference or
velocity pressure at the same value as was measured during the
steady-state dry coil test. The pressure difference or velocity
pressure should be within 2 percent of the value from the steady-
state dry coil test within 15 seconds after airflow initiation. For
units having a variable-speed indoor blower that ramps when cycling
on and/or off, use the exhaust fan of the airflow measuring
apparatus to impose a step response that begins at the initiation of
ramp up and ends at the termination of ramp down.
d. For units having a variable-speed indoor blower, conduct the
cyclic dry coil test using the pull-thru approach described below if
any of the following occur when testing with the fan operating:
(1) The test unit automatically cycles off;
(2) Its blower motor reverses; or
(3) The unit operates for more than 30 seconds at an external
static pressure that is 0.1 inches of water or more higher than the
value measured during the prior steady-state test.
For the pull-thru approach, disable the indoor blower and use
the exhaust fan of the airflow measuring apparatus to generate the
specified flow nozzles static pressure difference or velocity
pressure. If the exhaust fan cannot deliver the required pressure
difference because of resistance created by the unpowered blower,
temporarily remove the blower.
e. Conduct a minimum of six complete compressor OFF/ON cycles
for a unit with a single-speed or two-speed compressor, and a
minimum of five complete compressor OFF/ON cycles for a unit with a
variable speed compressor. The first three cycles for a unit with a
single-speed compressor or two-speed compressor and the first two
cycles for a unit with a unit with a variable speed compressor are
the warm-up period--the later cycles are called the active cycles.
Calculate the degradation coefficient CD for each
complete active cycle if the test tolerances given in Table 9 are
satisfied. If the average CD for the first three active
cycles is within 0.02 of the average CD for the first two
active cycles, use the average CD of the three active
cycles as the final result. If these averages differ by more than
0.02, continue the test to get CD for the fourth cycle.
If the average CD of the last three cycles is lower than
or no more than 0.02 greater than the average CD of the
first three cycles, use the average CD of all four active
cycles as the final result. Otherwise, continue the test with a
fifth cycle. If the average CD of the last three cycles
is 0.02 higher than the average for the previous three cycles, use
the default CD, otherwise use the average CD
of all five active cycles. If the test tolerances given in Table 9
are not satisfied, use default CD value. The default
CD value for cooling is 0.2.
f. With regard to the Table 9 parameters, continuously record
the dry-bulb temperature of the air entering the indoor and outdoor
coils during periods when air flows through the respective coils.
Sample the water vapor content of the indoor coil inlet air at least
every 2 minutes during periods when air flows through the coil.
Record external static pressure and the air volume rate indicator
(either nozzle pressure difference or velocity pressure) at least
every minute during the interval that air flows through the indoor
coil. (These regular measurements of the airflow rate indicator are
in addition to the required measurement at 15 seconds after flow
initiation.) Sample the electrical voltage at least every 2 minutes
beginning 30 seconds after compressor start-up. Continue until the
compressor, the outdoor fan, and the indoor blower (if it is
installed and operating) cycle off.
g. For ducted units, continuously record the dry-bulb
temperature of the air entering (as noted above) and leaving the
indoor coil. Or if using a thermopile, continuously record the
difference between these two temperatures during the interval that
air flows through the indoor coil. For non-ducted units, make the
same dry-bulb temperature measurements beginning when the compressor
cycles on and ending when indoor coil airflow ceases.
h. Integrate the electrical power over complete cycles of length
[Delta][tau]cyc,dry. For ducted units tested with an
indoor blower installed and operating, integrate electrical power
from indoor blower OFF to indoor blower OFF. For all other ducted
units and for non-ducted units, integrate electrical power from
compressor OFF to compressor OFF. (Some cyclic tests will use the
same data collection intervals to determine the electrical energy
[[Page 69363]]
and the total space cooling. For other units, terminate data
collection used to determine the electrical energy before
terminating data collection used to determine total space cooling.)
Table 9--Test Operating and Test Condition Tolerances for Cyclic Dry
Coil Cooling Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor entering dry-bulb temperature 2.0 0.5
\2\, [deg]F............................
Indoor entering wet-bulb temperature, .............. (\3\)
[deg]F.................................
Outdoor entering dry-bulb temperature 2.0 0.5
\2\, [deg]F............................
External resistance to airflow \2\, 0.12 ..............
inches of water........................
Airflow nozzle pressure difference or 8.0 \4\2.0
velocity pressure \2\, % of reading....
Electrical voltage \5\, % of rdg........ 2.0 1.5
------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Applies during the interval that air flows through the indoor
(outdoor) coil except for the first 30 seconds after flow initiation.
For units having a variable-speed indoor blower that ramps, the
tolerances listed for the external resistance to airflow apply from 30
seconds after achieving full speed until ramp down begins.
\3\ Shall at no time exceed a wet-bulb temperature that results in
condensate forming on the indoor coil.
\4\ The test condition shall be the average nozzle pressure difference
or velocity pressure measured during the steady-state dry coil test.
\5\ Applies during the interval when at least one of the following--the
compressor, the outdoor fan, or, if applicable, the indoor blower--are
operating except for the first 30 seconds after compressor start-up.
i. If the Table 9 tolerances are satisfied over the complete
cycle, record the measured electrical energy consumption as
ecyc,dry and express it in units of watt-hours. Calculate
the total space cooling delivered, qcyc,dry, in units of
Btu using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.018
where vi, Cp,a, vn' (or vn),
Wn, and FCD* are the values recorded during
the section 3.4 dry coil steady-state test and
Tal([tau]) = dry bulb temperature of the air entering
the indoor coil at time [tau], [deg]F.
Ta2([tau]) = dry bulb temperature of the air leaving
the indoor coil at time [tau], [deg]F.
[tau]1 = for ducted units, the elapsed time when
airflow is initiated through the indoor coil; for non-ducted units,
the elapsed time when the compressor is cycled on, hr.
[tau]2 = the elapsed time when indoor coil airflow
ceases, hr.
3.5.1 Procedures when testing ducted systems.
The automatic controls that are normally installed with the test
unit must govern the OFF/ON cycling of the air moving equipment on
the indoor side (exhaust fan of the airflow measuring apparatus and,
if installed, the indoor blower of the test unit). For example, for
ducted units tested without an indoor blower installed but rated
based on using a fan time delay relay, control the indoor coil
airflow according to the rated ON and/or OFF delays provided by the
relay. For ducted units having a variable-speed indoor blower that
has been disabled (and possibly removed), start and stop the indoor
airflow at the same instances as if the fan were enabled. For all
other ducted units tested without an indoor blower installed, cycle
the indoor coil airflow in unison with the cycling of the
compressor. If air damper boxes are used, close them on the inlet
and outlet side during the OFF period. Airflow through the indoor
coil should stop within 3 seconds after the automatic controls of
the test unit (act to) de-energize the indoor blower. For ducted
units tested without an indoor blower installed (excluding the
special case where a variable-speed fan is temporarily removed),
increase ecyc,dry by the quantity,
[GRAPHIC] [TIFF OMITTED] TP09NO15.019
where Vis is the average indoor air volume rate from the
section 3.4 dry coil steady-state test and is expressed in units of
cubic feet per minute of standard air (scfm). For units having a
variable-speed indoor blower that is disabled during the cyclic
test, increase ecyc,dry and decrease qcyc,dry
based on:
a. The product of [[tau]2 - [tau]1] and the indoor
blower power measured during or following the dry coil steady-state
test; or,
b. The following algorithm if the indoor blower ramps its speed
when cycling.
1. Measure the electrical power consumed by the variable-speed
indoor blower at a minimum of three operating conditions: At the
speed/air volume rate/external static pressure that was measured
during the steady-state test, at operating conditions associated
with the midpoint of the ramp-up interval, and at conditions
associated with the midpoint of the ramp-down interval. For these
measurements, the tolerances on the airflow volume or the external
static pressure are the same as required for the section 3.4 steady-
state test.
2. For each case, determine the fan power from measurements made
over a minimum of 5 minutes.
3. Approximate the electrical energy consumption of the indoor
blower if it had operated during the cyclic test using all three
power measurements. Assume a linear profile during the ramp
intervals. The manufacturer must provide the durations of the ramp-
up and ramp-down intervals. If the test setup instructions included
with the unit by the manufacturer specifies a ramp interval that
exceeds 45 seconds, use a 45-second ramp interval nonetheless when
estimating the fan energy.
3.5.2 Procedures when testing non-ducted systems.
[[Page 69364]]
Do not use airflow prevention devices when conducting cyclic
tests on non-ducted units. Until the last OFF/ON compressor cycle,
airflow through the indoor coil must cycle off and on in unison with
the compressor. For the last OFF/ON compressor cycle--the one used
to determine ecyc,dry and qcyc,dry--use the
exhaust fan of the airflow measuring apparatus and the indoor blower
of the test unit to have indoor airflow start 3 minutes prior to
compressor cut-on and end three minutes after compressor cutoff.
Subtract the electrical energy used by the indoor blower during the
3 minutes prior to compressor cut-on from the integrated electrical
energy, ecyc,dry. Add the electrical energy used by the
indoor blower during the 3 minutes after compressor cutoff to the
integrated cooling capacity, qcyc,dry. For the case where
the non-ducted unit uses a variable-speed indoor blower which is
disabled during the cyclic test, correct ecyc,dry and
qcyc,dry using the same approach as prescribed in section
3.5.1 for ducted units having a disabled variable-speed indoor
blower.
3.5.3 Cooling-mode cyclic-degradation coefficient calculation.
Use the two dry-coil tests to determine the cooling-mode cyclic-
degradation coefficient, CD\c\. Append ``(k=2)'' to the
coefficient if it corresponds to a two-capacity unit cycling at high
capacity. The default value for two-capacity units cycling at high
capacity, however, is the low-capacity coefficient, i.e.,
CD\c\(k=2) = CD\c\. Evaluate CD\c\
using the above results and those from the section 3.4 dry-coil
steady-state test.
[GRAPHIC] [TIFF OMITTED] TP09NO15.020
the average energy efficiency ratio during the cyclic dry coil
cooling mode test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TP09NO15.021
the average energy efficiency ratio during the steady-state dry coil
cooling mode test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TP09NO15.022
the cooling load factor dimensionless
Round the calculated value for CD\c\ to the nearest
0.01. If CD\c\ is negative, then set it equal to zero.
3.6 Heating mode tests for different types of heat pumps,
including heating-only heat pumps.
3.6.1 Tests for a heat pump having a single-speed compressor
that is tested with a fixed speed indoor blower installed, with a
constant-air-volume-rate indoor blower installed, or with no indoor
blower installed. Conduct the High Temperature Cyclic (H1C) Test to
determine the heating mode cyclic-degradation coefficient,
CD\h\. Test conditions for the four tests are specified
in Table 10.
Table 10--Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor
Blower, a Constant Air Volume Rate Indoor Blower, or No Indoor Blower
----------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F) Heating air
Test description ---------------------------------------------------------------- volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
----------------------------------------------------------------------------------------------------------------
H1 Test (required, steady).... 70 60\(max)\ 47 43 Heating Full-
load.\1\
H1C Test (required, cyclic)... 70 60\(max)\ 47 43 (\2\).
H2 Test (required)............ 70 60\(max)\ 35 33 Heating Full-
load.\1\
H3 Test (required, steady).... 70 60\(max)\ 17 15 Heating Full-
load.\1\
----------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4.
\2\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the
same pressure difference or velocity pressure as measured during the H1 Test.
3.6.2 Tests for a heat pump having a single-speed compressor and
a single indoor unit having either (1) a variable speed, variable-
air-rate indoor blower whose capacity modulation correlates with
outdoor dry bulb temperature or (2) multiple blowers. Conduct five
tests: Two High Temperature Tests (H12 and
H11), one Frost Accumulation Test (H22), and
two Low Temperature Tests (H32 and H31).
Conducting an additional Frost Accumulation Test (H21) is
optional. Conduct the High Temperature Cyclic (H1C1) Test
to determine the heating mode cyclic-degradation coefficient,
CD\h\. Test conditions for the seven tests are specified
in Table 11. If the optional H21 Test is not performed,
use the following equations to approximate the capacity and
electrical power of the heat pump at the H21 test
conditions:
[GRAPHIC] [TIFF OMITTED] TP09NO15.023
where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.024
[[Page 69365]]
The quantities Qh\k=2\(47), [Edot]h\k=2\(47),
Qh\k=1\(47), and [Edot]h\k=1\(47) are
determined from the H12 and H11 Tests and
evaluated as specified in section 3.7; the quantities
Qh\k=2\(35) and [Edot]h\k=2\(35) are
determined from the H22 Test and evaluated as specified
in section 3.9; and the quantities Qh\k=2\(17),
[Edot]h\k=2\(17), Qh\k=1\(17), and
[Edot]h\k=1\(17), are determined from the H32
and H31 Tests and evaluated as specified in section 3.10.
Table 11--Heating Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.6.2
Indoor Unit Requirements
----------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F) Heating air
Test description ---------------------------------------------------------------- volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
----------------------------------------------------------------------------------------------------------------
H12 Test (required, steady)... 70 60\(max)\ 47 43 Heating Full-
load.\1\
H11 Test (required, steady)... 70 60\(max)\ 47 43 Heating
Minimum.\2\
H1C1 Test (required, cyclic).. 70 60\(max)\ 47 43 (\3\)
H22 Test (required)........... 70 60\(max)\ 35 33 Heating Full-
load.\1\
H21 Test (optional)........... 70 60\(max)\ 35 33 Heating
Minimum.\2\
H32 Test (required, steady)... 70 60\(max)\ 17 15 Heating Full-
load.\1\
H31 Test (required, steady)... 70 60\(max)\ 17 15 Heating
Minimum.\2\
----------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4.
\2\ Defined in section 3.1.4.5.
\3\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the
same pressure difference or velocity pressure as measured during the H11 Test.
3.6.3 Tests for a heat pump having a two-capacity compressor
(see section 1.2, Definitions), including two-capacity, northern
heat pumps (see section 1.2, Definitions).
a. Conduct one Maximum Temperature Test (H01), two
High Temperature Tests (H12and H11), one Frost
Accumulation Test (H22), and one Low Temperature Test
(H32). Conduct an additional Frost Accumulation Test
(H21) and Low Temperature Test (H31) if both
of the following conditions exist:
1. Knowledge of the heat pump's capacity and electrical power at
low compressor capacity for outdoor temperatures of 37 [deg]F and
less is needed to complete the section 4.2.3 seasonal performance
calculations; and
2. The heat pump's controls allow low-capacity operation at
outdoor temperatures of 37 [deg]F and less.
If the above two conditions are met, an alternative to
conducting the H21 Frost Accumulation is to use the
following equations to approximate the capacity and electrical
power:
[GRAPHIC] [TIFF OMITTED] TP09NO15.025
Determine the quantities Qh\k=1\ (47) and
[Edot]h\k=1\ (47) from the H11 Test and
evaluate them according to Section 3.7. Determine the quantities
Qh\k=1\ (17) and [Edot]h\k=1\ (17) from the
H31 Test and evaluate them according to Section 3.10.
b. Conduct the High Temperature Cyclic Test (H1C1) to
determine the heating mode cyclic-degradation coefficient,
CD\h\. If a two-capacity heat pump locks out low capacity
operation at lower outdoor temperatures, conduct the High
Temperature Cyclic Test (H1C2) to determine the high-
capacity heating mode cyclic-degradation coefficient,
CD\h\ (k=2). The default CD\h\ (k=2) is the
same value as determined or assigned for the low-capacity cyclic-
degradation coefficient, CD\h\ [or equivalently,
CD\h\ (k=1)]. Table 12 specifies test conditions for
these nine tests.
Table 12--Heating Mode Test Conditions for Units Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Compressor capacity Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).......... 70 60 \(max)\ 62 56.5 Low..................... Heating Minimum.\1\
H12 Test (required, steady).......... 70 60 \(max)\ 47 43 High.................... Heating Full-Load.\2\
H1C2 Test (required,\7\ cyclic)...... 70 60 \(max)\ 47 43 High.................... (\3\).
H11 Test (required).................. 70 60 \(max)\ 47 43 Low..................... Heating Minimum.\1\
H1C1 Test (required, cyclic)......... 70 60 \(max)\ 47 43 Low..................... (\4\).
H22 Test (required).................. 70 60 \(max)\ 35 33 High.................... Heating Full-Load.\2\
H21 Test 5 6 (required).............. 70 60 \(max)\ 35 33 Low..................... Heating Minimum.\1\
H32 Test (required, steady).......... 70 60 \(max)\ 17 15 High.................... Heating Full-Load.\2\
[[Page 69366]]
H31 Test \5\ (required, steady)...... 70 60 \(max)\ 17 15 Low..................... Heating Minimum.\1\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5.
\2\ Defined in section 3.1.4.4.
\3\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H12 Test.
\4\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H11 Test.
\5\ Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 [deg]F is needed to
complete the section 4.2.3 HSPF calculations.
\6\ If table note #5 applies, the section 3.6.3 equations for Qh\k=1\ (35) and [Edot]h\k=1\ (17) may be used in lieu of conducting the H21 Test.
\7\ Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.
3.6.4 Tests for a heat pump having a variable-speed compressor.
a. Conduct one Maximum Temperature Test (H01), two
High Temperature Tests (H12 and H11), one
Frost Accumulation Test (H2V), and one Low Temperature
Test (H32). Conducting one or both of the following tests
is optional: An additional High Temperature Test (H1N)
and an additional Frost Accumulation Test (H22). Conduct
the Maximum Temperature Cyclic (H0C1) Test to determine
the heating mode cyclic-degradation coefficient, CD\h\.
Test conditions for the eight tests are specified in Table 13.
Determine the intermediate compressor speed cited in Table 13 using
the heating mode maximum and minimum compressors speeds and:
[GRAPHIC] [TIFF OMITTED] TP09NO15.026
Where a tolerance of plus 5 percent or the next higher inverter
frequency step from that calculated is allowed. If the
H22Test is not done, use the following equations to
approximate the capacity and electrical power at the H22
test conditions:
[GRAPHIC] [TIFF OMITTED] TP09NO15.027
b. Determine the quantities Qh\k=2\(47) and from
[Edot]h\k=2\(47) from the H12 Test and
evaluate them according to section 3.7. Determine the quantities
Qh\k=2\(17) and [Edot]h\k=2\(17) from the
H32 Test and evaluate them according to section 3.10. For
heat pumps where the heating mode maximum compressor speed exceeds
its cooling mode maximum compressor speed, conduct the
H1N Test if the manufacturer requests it. If the
H1N Test is done, operate the heat pump's compressor at
the same speed as the speed used for the cooling mode A2
Test. Refer to the last sentence of section 4.2 to see how the
results of the H1N Test may be used in calculating the
heating seasonal performance factor.
Table 13--Heating Mode Test Conditions for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Compressor speed Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).......... 70 60 \(max)\ 62 56.5 Minimum................. Heating Minimum.\1\
H0C1 Test (required, steady)......... 70 60 \(max)\ 62 56.5 Minimum................. (\2\).
H12 Test (required, steady).......... 70 60 \(max)\ 47 43 Maximum................. Heating Full-Load.\3\
H11 Test (required, steady).......... 70 60 \(max)\ 47 43 Minimum................. Heating Minimum.\1\
H1N Test (optional, steady).......... 70 60 \(max)\ 47 43 Cooling Mode Maximum.... Heating Nominal.\4\
H22 Test (optional).................. 70 60 \(max)\ 35 33 Maximum................. Heating Full-Load.\3\
H2V Test (required).................. 70 60 \(max)\ 35 33 Intermediate............ Heating
Intermediate.\5\
H32 Test (required, steady).......... 70 60 \(max)\ 17 15 Maximum................. Heating Full-Load.\3\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5.
\2\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured
during the H01 Test.
[[Page 69367]]
\3\ Defined in section 3.1.4.4.
\4\ Defined in section 3.1.4.7.
\5\ Defined in section 3.1.4.6.
c. For multiple-split heat pumps (only), the following
procedures supersede the above requirements. For all Table 13 tests
specified for a minimum compressor speed, at least one indoor unit
must be turned off. The manufacturer shall designate the particular
indoor unit(s) that is turned off. The manufacturer must also
specify the compressor speed used for the Table 13 H2V
Test, a heating mode intermediate compressor speed that falls within
\1/4\ and \3/4\ of the difference between the maximum and minimum
heating mode speeds. The manufacturer should prescribe an
intermediate speed that is expected to yield the highest COP for the
given H2V Test conditions and bracketed compressor speed
range. The manufacturer can designate that one or more specific
indoor units are turned off for the H2V Test.
3.6.5 Additional test for a heat pump having a heat comfort
controller.
Test any heat pump that has a heat comfort controller (see
section 1.2, Definitions) according to section 3.6.1, 3.6.2, or
3.6.3, whichever applies, with the heat comfort controller disabled.
Additionally, conduct the abbreviated test described in section
3.1.9 with the heat comfort controller active to determine the
system's maximum supply air temperature. (Note: Heat pumps having a
variable speed compressor and a heat comfort controller are not
covered in the test procedure at this time.)
3.6.6 Heating mode tests for northern heat pumps with triple-
capacity compressors.
Test triple-capacity, northern heat pumps for the heating mode
as follows:
(a) Conduct one maximum-temperature test (H01), two
high-temperature tests (H12 and H11), one
Frost Accumulation test (H22), two low-temperature tests
(H32, H33), and one minimum-temperature test
(H43). Conduct an additional Frost Accumulation test
(H21) and low- temperature test (H31) if both
of the following conditions exist: (1) Knowledge of the heat pump's
capacity and electrical power at low compressor capacity for outdoor
temperatures of 37 [deg]F and less is needed to complete the section
4.2.6 seasonal performance calculations; and (2) the heat pump's
controls allow low-capacity operation at outdoor temperatures of 37
[deg]F and less. If the above two conditions are met, an alternative
to conducting the H21 Frost Accumulation Test to
determine Qh\k=1\(35) and [Edot]h\k=1\(35) is
to use the following equations to approximate this capacity and
electrical power:
[GRAPHIC] [TIFF OMITTED] TP09NO15.028
In evaluating the above equations, determine the quantities
Qh\k=1\(47) from the H11 Test and evaluate
them according to section 3.7. Determine the quantities
Qh\k=1\(17) and [Edot]h\k=1\(17) from the
H31 Test and evaluate them according to section 3.10. Use
the paired values of Qh\k=1\(35) and
[Edot]h\k=1\(35) derived from conducting the
H21 Frost Accumulation Test and evaluated as specified in
section 3.9.1 or use the paired values calculated using the above
default equations, whichever contribute to a higher Region IV HSPF
based on the DHRmin.
(b) Conducting a Frost Accumulation Test (H23) with
the heat pump operating at its booster capacity is optional. If this
optional test is not conducted, determine Qh\k=3\(35) and
Eh\k=3\(35) using the following equations to approximate
this capacity and electrical power:
[GRAPHIC] [TIFF OMITTED] TP09NO15.029
where:
[GRAPHIC] [TIFF OMITTED] TP09NO15.030
Determine the quantities Qh\k=2\(47) and
[Edot]h\k=2\(47) from the H12 Test and
evaluate them according to section 3.7. Determine the quantities
Qh\k=2\(35) and [Edot]h\k=2\(35) from the
H22Test and evaluate them according to section 3.9.1.
Determine the quantities Qh\k=2\(17) and
[Edot]h\k=2\(17) from the H32Test, determine
the quantities Qh\k=3\(17) and
[Edot]h\k=3\(17) from the H33Test, and
determine the quantities Qh\k=3\(2) and
[Edot]h\k=3\(2) from the H43Test. Evaluate all
six quantities according to section 3.10. Use the paired values of
Qh\k=3\(35) and [Edot]h\k=3\(35) derived from
conducting the H23Frost Accumulation Test and calculated
as specified in section 3.9.1 or use the paired values calculated
using the above default equations, whichever contribute to a higher
Region IV HSPF based on the DHRmin.
(c) Conduct the high-temperature cyclic test (H1C1)
to determine the heating mode cyclic-degradation coefficient,
CD\h\. If a triple-capacity heat pump locks out low
capacity operation at lower outdoor temperatures, conduct the high-
temperature cyclic test (H1C2) to determine the high-
capacity heating mode cyclic-degradation coefficient,
CD\h\ (k=2). The default CD\h\ (k=2) is the
same value as determined or assigned for the low-capacity cyclic-
degradation coefficient, CD\h\ [or equivalently,
CD\h\ (k=1)]. Finally, if a triple-capacity heat pump
locks out both low and high capacity operation at the lowest outdoor
temperatures, conduct the low-temperature cyclic test
(H3C3) to determine the booster-capacity heating mode
cyclic-
[[Page 69368]]
degradation coefficient, CD\h\ (k=3). The default
CD\h\ (k=3) is the same value as determined or assigned
for the high-capacity cyclic-degradation coefficient,
CD\h\ [or equivalently, CD\h\ (k=2)]. Table 14
specifies test conditions for all 13 tests.
Table 14--Heating Mode Test Conditions for Units With a Triple-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Compressor capacity Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).......... 70 60 \(max)\ 62 56.5 Low..................... Heating Minimum.\1\
H12 Test (required, steady).......... 70 60 \(max)\ 47 43 High.................... Heating Full-Load.\2\
H1C2 Test (required,\8\ cyclic)...... 70 60 \(max)\ 47 43 High.................... \3\.
H11 Test (required).................. 70 60 \(max)\ 47 43 Low..................... Heating Minimum \1\.
H1C1 Test (required, cyclic)......... 70 60 \(max)\ 47 43 Low..................... \4\.
H23 Test (optional, steady).......... 70 60 \(max)\ 35 33 Booster................. Heating Full-Load.\2\
H22 Test (required).................. 70 60 \(max)\ 35 33 High.................... Heating Full-Load.\2\
H21 Test (required).................. 70 60 \(max)\ 35 33 Low..................... Heating Minimum.\1\
H33 Test (required, steady).......... 70 60 \(max)\ 17 15 Booster................. Heating Full-Load.\2\
H3C3 Test \5 6\ (required, cyclic)... 70 60 \(max)\ 17 15 Booster................. \7\.
H32 Test (required, steady).......... 70 60 \(max)\ 17 15 High.................... Heating Full-Load.\2\
H31 Test \5\ (required, steady)...... 70 60 \(max)\ 17 15 Low..................... Heating Minimum.\1\
H43 Test (required, steady).......... 70 60 \(max)\ 2 1 Booster................. Heating Full-Load.\2\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5.
\2\ Defined in section 3.1.4.4.
\3\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H12 Test.
\4\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H11Test.
\5\ Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 [deg]F is needed to
complete the section 4.2.6 HSPF calculations.
\6\ If table note \5\ applies, the section 3.6.6 equations for Qh\k=1\ (35) and [Edot]h\k=1\ (17) may be used in lieu of conducting the H21 Test.
\7\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H33 Test.
\8\ Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.
3.6.7 Tests for a heat pump having a single indoor unit having
multiple blowers and offering two stages of compressor modulation.
Conduct the heating mode tests specified in section 3.6.3.
3.7 Test procedures for steady-state Maximum Temperature and
High Temperature heating mode tests (the H01, H1,
H12, H11, and H1N Tests).
a. For the pretest interval, operate the test room
reconditioning apparatus and the heat pump until equilibrium
conditions are maintained for at least 30 minutes at the specified
section 3.6 test conditions. Use the exhaust fan of the airflow
measuring apparatus and, if installed, the indoor blower of the heat
pump to obtain and then maintain the indoor air volume rate and/or
the external static pressure specified for the particular test.
Continuously record the dry-bulb temperature of the air entering the
indoor coil, and the dry-bulb temperature and water vapor content of
the air entering the outdoor coil. Refer to section 3.11 for
additional requirements that depend on the selected secondary test
method. After satisfying the pretest equilibrium requirements, make
the measurements specified in Table 3 of ASHRAE Standard 37-2009
(incorporated by reference, see Sec. 430.3) for the Indoor Air
Enthalpy method and the user-selected secondary method. Make said
Table 3 measurements at equal intervals that span 5 minutes or less.
Continue data sampling until a 30-minute period (e.g., four
consecutive 10-minute samples) is reached where the test tolerances
specified in Table 15 are satisfied. For those continuously recorded
parameters, use the entire data set for the 30-minute interval when
evaluating Table 15 compliance. Determine the average electrical
power consumption of the heat pump over the same 30-minute interval.
Table 15--Test Operating and Test Condition Tolerances for Section 3.7
and Section 3.10 Steady-State Heating Mode Tests
------------------------------------------------------------------------
Test Test
operating condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor dry-bulb, [deg]F:
Entering temperature.................. 2.0 0.5
Leaving temperature................... 2.0 .............
Indoor wet-bulb, [deg]F:
Entering temperature.................. 1.0 .............
Leaving temperature................... 1.0 .............
Outdoor dry-bulb, [deg]F:
[[Page 69369]]
Entering temperature.................. 2.0 0.5
Leaving temperature................... \2\ 2.0 .............
Outdoor wet-bulb, [deg]F:
Entering temperature.................. 1.0 0.3
Leaving temperature................... \2\ 1.0 .............
External resistance to airflow, inches of 0.12 \3\ 0.02
water....................................
Electrical voltage, % of rdg.......... 2.0 1.5
Nozzle pressure drop, % of rdg........ 8.0 .............
------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Only applies when the Outdoor Air Enthalpy Method is used.
\3\ Only applies when testing non-ducted units.
b. Calculate indoor-side total heating capacity as specified in
sections 7.3.4.1 and 7.3.4.3 of ASHRAE Standard 37-2009
(incorporated by reference, see Sec. 430.3). Do not adjust the
parameters used in calculating capacity for the permitted variations
in test conditions. Assign the average space heating capacity and
electrical power over the 30-minute data collection interval to the
variables Qh\k\ and [Edot]h\k\(T)
respectively. The ``T'' and superscripted ``k'' are the same as
described in section 3.3. Additionally, for the heating mode, use
the superscript to denote results from the optional H1N
Test, if conducted.
c. For heat pumps tested without an indoor blower installed,
increase Qh\k\(T) by
[GRAPHIC] [TIFF OMITTED] TP09NO15.031
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
During the 30-minute data collection interval of a High Temperature
Test, pay attention to preventing a defrost cycle. Prior to this
time, allow the heat pump to perform a defrost cycle if
automatically initiated by its own controls. As in all cases, wait
for the heat pump's defrost controls to automatically terminate the
defrost cycle. Heat pumps that undergo a defrost should operate in
the heating mode for at least 10 minutes after defrost termination
prior to beginning the 30-minute data collection interval. For some
heat pumps, frost may accumulate on the outdoor coil during a High
Temperature test. If the indoor coil leaving air temperature or the
difference between the leaving and entering air temperatures
decreases by more than 1.5 [deg]F over the 30-minute data collection
interval, then do not use the collected data to determine capacity.
Instead, initiate a defrost cycle. Begin collecting data no sooner
than 10 minutes after defrost termination. Collect 30 minutes of new
data during which the Table 15 test tolerances are satisfied. In
this case, use only the results from the second 30-minute data
collection interval to evaluate Qh\k\(47) and
[Edot]h\k\(47).
d. If conducting the cyclic heating mode test, which is
described in section 3.8, record the average indoor-side air volume
rate, Vi, specific heat of the air, Cp,a (expressed on
dry air basis), specific volume of the air at the nozzles,
vn' (or vn), humidity ratio at the nozzles,
Wn, and either pressure difference or velocity pressure
for the flow nozzles. If either or both of the below criteria apply,
determine the average, steady-state, electrical power consumption of
the indoor blower motor ([Edot]fan,1):
1. The section 3.8 cyclic test will be conducted and the heat
pump has a variable-speed indoor blower that is expected to be
disabled during the cyclic test; or
2. The heat pump has a (variable-speed) constant-air volume-rate
indoor blower and during the steady-state test the average external
static pressure ([Delta]P1) exceeds the applicable
section 3.1.4.4 minimum (or targeted) external static pressure
([Delta]Pmin) by 0.03 inches of water or more.
Determine [Edot]fan,1 by making measurements during
the 30-minute data collection interval, or immediately following the
test and prior to changing the test conditions. When the above ``2''
criteria applies, conduct the following four steps after determining
[Edot]fan,1 (which corresponds to [Delta]P1):
i. While maintaining the same test conditions, adjust the
exhaust fan of the airflow measuring apparatus until the external
static pressure increases to approximately [Delta]P1 +
([Delta]P1 - [Delta]Pmin).
ii. After re-establishing steady readings for fan motor power
and external static pressure, determine average values for the
indoor blower power ([Edot]fan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
iii. Approximate the average power consumption of the indoor
blower motor if the 30-minute test had been conducted at
[Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TP09NO15.032
iv. Decrease the total space heating capacity,
Qh\k\(T), by the quantity ([Edot]fan,1 -
[Edot]fan,min), when expressed on a Btu/h basis. Decrease
the total electrical power, [Edot]h\k\(T) by the same fan
power difference, now expressed in watts.
e. If the temperature sensors used to provide the primary
measurement of the indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the subsequent cyclic dry-
coil test are different, include measurements of the latter sensors
among the regularly sampled data. Beginning at the start of the 30-
minute data collection period, measure and compute the indoor-side
air dry-bulb temperature difference using both sets of
instrumentation, [Delta]T (Set SS) and [Delta]T (Set CYC), for each
equally spaced data sample. If using a consistent data sampling rate
that is less than 1 minute, calculate and record minutely averages
for the two temperature differences. If using a consistent sampling
rate of one minute or more, calculate and record the two temperature
differences from each data sample. After having recorded the seventh
(i=7) set of temperature differences, calculate the following ratio
using the first seven sets of values:
[[Page 69370]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.033
Each time a subsequent set of temperature differences is
recorded (if sampling more frequently than every 5 minutes),
calculate FCD using the most recent seven sets of values.
Continue these calculations until the 30-minute period is completed
or until a value for FCD is calculated that falls outside
the allowable range of 0.94-1.06. If the latter occurs, immediately
suspend the test and identify the cause for the disparity in the two
temperature difference measurements. Recalibration of one or both
sets of instrumentation may be required. If all the values for
FCD are within the allowable range, save the final value
of the ratio from the 30-minute test as FCD*. If the
temperature sensors used to provide the primary measurement of the
indoor-side dry bulb temperature difference during the steady-state
dry-coil test and the subsequent cyclic dry-coil test are the same,
set FCD*= 1.
3.8 Test procedures for the cyclic heating mode tests (the
H0C1, H1C, H1C1 and H1C2 Tests).
a. Except as noted below, conduct the cyclic heating mode test
as specified in section 3.5. As adapted to the heating mode, replace
section 3.5 references to ``the steady-state dry coil test'' with
``the heating mode steady-state test conducted at the same test
conditions as the cyclic heating mode test.'' Use the test
tolerances in Table 16 rather than Table 9. Record the outdoor coil
entering wet-bulb temperature according to the requirements given in
section 3.5 for the outdoor coil entering dry-bulb temperature. Drop
the subscript ``dry'' used in variables cited in section 3.5 when
referring to quantities from the cyclic heating mode test., The
default CD value for heating is 0.25. If available, use
electric resistance heaters (see section 2.1) to minimize the
variation in the inlet air temperature. Determine the total space
heating delivered during the cyclic heating test, qcyc,
as specified in section 3.5 except for making the following changes:
(1) When evaluating Equation 3.5-1, use the values of Vi,
Cp,a,vn', (or vn), and
Wn that were recorded during the section 3.7 steady-state
test conducted at the same test conditions.
(2) Calculate [Gamma] using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.034
where FCD* is the value recorded during the section 3.7
steady-state test conducted at the same test condition.
b. For ducted heat pumps tested without an indoor blower
installed (excluding the special case where a variable-speed fan is
temporarily removed), increase qcyc by the amount
calculated using Equation 3.5-3. Additionally, increase
ecyc by the amount calculated using Equation 3.5-2. In
making these calculations, use the average indoor air volume rate
(Vis) determined from the section 3.7 steady-state
heating mode test conducted at the same test conditions.
c. For non-ducted heat pumps, subtract the electrical energy
used by the indoor blower during the 3 minutes after compressor
cutoff from the non-ducted heat pump's integrated heating capacity,
qcyc.
d. If a heat pump defrost cycle is manually or automatically
initiated immediately prior to or during the OFF/ON cycling, operate
the heat pump continuously until 10 minutes after defrost
termination. After that, begin cycling the heat pump immediately or
delay until the specified test conditions have been re-established.
Pay attention to preventing defrosts after beginning the cycling
process. For heat pumps that cycle off the indoor blower during a
defrost cycle, make no effort here to restrict the air movement
through the indoor coil while the fan is off. Resume the OFF/ON
cycling while conducting a minimum of two complete compressor OFF/ON
cycles before determining qcyc and ecyc.
3.8.1 Heating mode cyclic-degradation coefficient calculation.
Use the results from the required cyclic test and the required
steady-state test that were conducted at the same test conditions to
determine the heating mode cyclic-degradation coefficient
CD\h\. Add ``(k=2)'' to the coefficient if it corresponds
to a two-capacity unit cycling at high capacity. For the below
calculation of the heating mode cyclic degradation coefficient, do
not include the duct loss correction from section 7.3.3.3 of ASHRAE
Standard 37-2009 (incorporated by reference, see Sec. 430.3) in
determining Qh\k\(Tcyc) (or qcyc).
The default value for two-capacity units cycling at high capacity,
however, is the low-capacity coefficient, i.e., CD\h\
(k=2) = CD\h\. The tested CDhis
calculated as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.035
Where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.036
the average coefficient of performance during the cyclic heating
mode test, dimensionless.
[GRAPHIC] [TIFF OMITTED] TP09NO15.037
[[Page 69371]]
the average coefficient of performance during the steady-state
heating mode test conducted at the same test conditions--i.e., same
outdoor dry bulb temperature, Tcyc, and speed/capacity,
k, if applicable--as specified for the cyclic heating mode test,
dimensionless.
[GRAPHIC] [TIFF OMITTED] TP09NO15.038
the heating load factor, dimensionless.
Tcyc = the nominal outdoor temperature at which the
cyclic heating mode test is conducted, 62 or 47 [deg]F.
[Delta][tau]cyc = the duration of the OFF/ON intervals;
0.5 hours when testing a heat pump having a single-speed or two-
capacity compressor and 1.0 hour when testing a heat pump having a
variable-speed compressor.
Round the calculated value for CD\h\ to the nearest
0.01. If CD\h\ is negative, then set it equal to zero.
Table 16--Test Operating and Test Condition Tolerances for Cyclic
Heating Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor entering dry-bulb temperature,\2\ 2.0 0.5
[deg]F.................................
Indoor entering wet-bulb temperature,\2\ 1.0 ..............
[deg]F.................................
Outdoor entering dry-bulb 2.0 0.5
temperature,\2\ [deg]F.................
Outdoor entering wet-bulb 2.0 1.0
temperature,\2\ [deg]F.................
External resistance to air-flow,\2\ 0.12 ..............
inches of water........................
Airflow nozzle pressure difference or 2.0 \3\ 2.0
velocity pressure,\2\% of reading......
Electrical voltage,\4\% of rdg.......... 8.0 1.5
------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Applies during the interval that air flows through the indoor
(outdoor) coil except for the first 30 seconds after flow initiation.
For units having a variable-speed indoor blower that ramps, the
tolerances listed for the external resistance to airflow shall apply
from 30 seconds after achieving full speed until ramp down begins.
\3\ The test condition shall be the average nozzle pressure difference
or velocity pressure measured during the steady-state test conducted
at the same test conditions.
\4\ Applies during the interval that at least one of the following--the
compressor, the outdoor fan, or, if applicable, the indoor blower--are
operating, except for the first 30 seconds after compressor start-up.
3.9 Test procedures for Frost Accumulation heating mode tests
(the H2, H22, H2V, and H21 Tests).
a. Confirm that the defrost controls of the heat pump are set as
specified in section 2.2.1. Operate the test room reconditioning
apparatus and the heat pump for at least 30 minutes at the specified
section 3.6 test conditions before starting the ``preliminary'' test
period. The preliminary test period must immediately precede the
``official'' test period, which is the heating and defrost interval
over which data are collected for evaluating average space heating
capacity and average electrical power consumption.
b. For heat pumps containing defrost controls which are likely
to cause defrosts at intervals less than one hour, the preliminary
test period starts at the termination of an automatic defrost cycle
and ends at the termination of the next occurring automatic defrost
cycle. For heat pumps containing defrost controls which are likely
to cause defrosts at intervals exceeding one hour, the preliminary
test period must consist of a heating interval lasting at least one
hour followed by a defrost cycle that is either manually or
automatically initiated. In all cases, the heat pump's own controls
must govern when a defrost cycle terminates.
c. The official test period begins when the preliminary test
period ends, at defrost termination. The official test period ends
at the termination of the next occurring automatic defrost cycle.
When testing a heat pump that uses a time-adaptive defrost control
system (see section 1.2, Definitions), however, manually initiate
the defrost cycle that ends the official test period at the instant
indicated by instructions provided by the manufacturer. If the heat
pump has not undergone a defrost after 6 hours, immediately conclude
the test and use the results from the full 6-hour period to
calculate the average space heating capacity and average electrical
power consumption.
For heat pumps that turn the indoor blower off during the
defrost cycle, take steps to cease forced airflow through the indoor
coil and block the outlet duct whenever the heat pump's controls
cycle off the indoor blower. If it is installed, use the outlet
damper box described in section 2.5.4.1 to affect the blocked outlet
duct.
d. Defrost termination occurs when the controls of the heat pump
actuate the first change in converting from defrost operation to
normal heating operation. Defrost initiation occurs when the
controls of the heat pump first alter its normal heating operation
in order to eliminate possible accumulations of frost on the outdoor
coil.
e. To constitute a valid Frost Accumulation test, satisfy the
test tolerances specified in Table 17 during both the preliminary
and official test periods. As noted in Table 17, test operating
tolerances are specified for two sub-intervals: (1) When heating,
except for the first 10 minutes after the termination of a defrost
cycle (Sub-interval H, as described in Table 17) and (2) when
defrosting, plus these same first 10 minutes after defrost
termination (Sub-interval D, as described in Table 17). Evaluate
compliance with Table 17 test condition tolerances and the majority
of the test operating tolerances using the averages from
measurements recorded only during Sub-interval H. Continuously
record the dry bulb temperature of the air entering the indoor coil,
and the dry bulb temperature and water vapor content of the air
entering the outdoor coil. Sample the remaining parameters listed in
Table 17 at equal intervals that span 5 minutes or less.
f. For the official test period, collect and use the following
data to calculate average space heating capacity and electrical
power. During heating and defrosting intervals when the controls of
the heat pump have the indoor blower on, continuously record the
dry-bulb temperature of the air entering (as noted above) and
leaving the indoor coil. If using a thermopile, continuously record
the difference between the leaving and entering dry-bulb
temperatures during the interval(s) that air flows through the
indoor coil. For heat pumps tested without an indoor blower
installed, determine the corresponding cumulative time (in hours) of
indoor coil airflow, [Delta][tau]a. Sample measurements
used in calculating the air volume rate (refer to sections 7.7.2.1
and 7.7.2.2 of ASHRAE Standard 37-2009) at equal intervals that span
10 minutes or less. (Note: In the first printing of ASHRAE Standard
37-2009, the second IP equation for Qmi should read:)
Record the electrical energy consumed, expressed in watt-hours, from
defrost termination to defrost termination,
eDEFk(35), as well as the corresponding
elapsed time in hours, [Delta][tau]FR.
[[Page 69372]]
Table 17--Test Operating and Test Condition Tolerances for Frost Accumulation Heating Mode Tests
----------------------------------------------------------------------------------------------------------------
Test operating tolerance \1\
------------------------------------- Test condition
Sub-interval H Sub-interval D tolerance \1\ Sub-
\2\ \3\ interval H\2\
----------------------------------------------------------------------------------------------------------------
Indoor entering dry-bulb temperature, [deg]F............ 2.0 \4\ 4.0 0.5
Indoor entering wet-bulb temperature, [deg]F............ 1.0 ................ .................
Outdoor entering dry-bulb temperature, [deg]F........... 2.0 10.0 1.0
Outdoor entering wet-bulb temperature, [deg]F........... 1.5 ................ 0.5
External resistance to airflow, inches of water......... 0.12 ................ \5\ 0.02
Electrical voltage, % of rdg............................ 2.0 ................ 1.5
----------------------------------------------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a
defrost cycle.
\3\ Applies during a defrost cycle and during the first 10 minutes after the termination of a defrost cycle when
the heat pump is operating in the heating mode.
\4\ For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies
during the 10 minute interval that follows defrost termination.
\5\ Only applies when testing non-ducted heat pumps.
3.9.1 Average space heating capacity and electrical power
calculations.
a. Evaluate average space heating capacity,
Qhk(35), when expressed in units of Btu per
hour, using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.039
Where,
Vi = the average indoor air volume rate measured during Sub-interval
H, cfm.
Cp,a = 0.24 + 0.444 [middot] Wn, the constant
pressure specific heat of the air-water vapor mixture that flows
through the indoor coil and is expressed on a dry air basis, Btu/
lbmda [middot] [deg]F.
vn' = specific volume of the air-water vapor mixture at
the nozzle, ft\3\/lbmmx.
Wn = humidity ratio of the air-water vapor mixture at the
nozzle, lbm of water vapor per lbm of dry air.
[Delta][tau]FR = [tau]2 - [tau]1,
the elapsed time from defrost termination to defrost termination,
hr.
[GRAPHIC] [TIFF OMITTED] TP09NO15.040
Tal([tau]) = dry bulb temperature of the air entering the
indoor coil at elapsed time [tau], [deg]F; only recorded when indoor
coil airflow occurs; assigned the value of zero during periods (if
any) where the indoor blower cycles off.
Ta2([tau]) = dry bulb temperature of the air leaving the
indoor coil at elapsed time [tau], [deg]F; only recorded when indoor
coil airflow occurs; assigned the value of zero during periods (if
any) where the indoor blower cycles off.
[tau]1 = the elapsed time when the defrost termination
occurs that begins the official test period, hr.
[tau]2 = the elapsed time when the next automatically
occurring defrost termination occurs, thus ending the official test
period, hr.
vn = specific volume of the dry air portion of the
mixture evaluated at the dry-bulb temperature, vapor content, and
barometric pressure existing at the nozzle, ft\3\ per lbm of dry
air.
To account for the effect of duct losses between the outlet of
the indoor unit and the section 2.5.4 dry-bulb temperature grid,
adjust Qhk(35) in accordance with section
7.3.4.3 of ASHRAE Standard 37-2009 (incorporated by reference, see
Sec. 430.3).
b. Evaluate average electrical power,
[Edot]hk(35), when expressed in units of
watts, using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.041
For heat pumps tested without an indoor blower installed,
increase Qhk(35) by,
[GRAPHIC] [TIFF OMITTED] TP09NO15.042
and increase [Edot]hk(35) by,
[[Page 69373]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.043
Where Vis is the average indoor air volume rate measured
during the Frost Accumulation heating mode test and is expressed in
units of cubic feet per minute of standard air (scfm).
c. For heat pumps having a constant-air-volume-rate indoor
blower, the five additional steps listed below are required if the
average of the external static pressures measured during sub-
Interval H exceeds the applicable section 3.1.4.4, 3.1.4.5, or
3.1.4.6 minimum (or targeted) external static pressure
([Delta]Pmin) by 0.03 inches of water or more:
1. Measure the average power consumption of the indoor blower
motor ([Edot]fan,1) and record the corresponding external
static pressure ([Delta]P1) during or immediately
following the Frost Accumulation heating mode test. Make the
measurement at a time when the heat pump is heating, except for the
first 10 minutes after the termination of a defrost cycle.
2. After the Frost Accumulation heating mode test is completed
and while maintaining the same test conditions, adjust the exhaust
fan of the airflow measuring apparatus until the external static
pressure increases to approximately [Delta]P1 +
([Delta]P1 - [Delta]Pmin).
3. After re-establishing steady readings for the fan motor power
and external static pressure, determine average values for the
indoor blower power ([Edot]fan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
4. Approximate the average power consumption of the indoor
blower motor had the Frost Accumulation heating mode test been
conducted at [Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TP09NO15.044
5. Decrease the total heating capacity,
Qhk(35), by the quantity
[([Edot]fan,1 -[Edot]fan,min)[middot]
([Delta][tau] a/[Delta][tau] FR], when
expressed on a Btu/h basis. Decrease the total electrical power,
Ehk(35), by the same quantity, now expressed
in watts.
3.9.2 Demand defrost credit.
a. Assign the demand defrost credit, Fdef, that is
used in section 4.2 to the value of 1 in all cases except for heat
pumps having a demand-defrost control system (see section 1.2,
Definitions). For such qualifying heat pumps, evaluate
Fdef using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.045
Where,
[Delta][tau]def = the time between defrost terminations
(in hours) or 1.5, whichever is greater. A value of 6 must be
assigned to [Delta][tau]def if this limit is reached
during a Frost Accumulation test and the heat pump has not completed
a defrost cycle.
[Delta][tau]max = maximum time between defrosts as
allowed by the controls (in hours) or 12, whichever is less, as
provided in the installation manuals included with the unit by the
manufacturer.
b. For two-capacity heat pumps and for section 3.6.2 units,
evaluate the above equation using the [Delta][tau]def
that applies based on the Frost Accumulation Test conducted at high
capacity and/or at the Heating Full-load Air Volume Rate. For
variable-speed heat pumps, evaluate [Delta][tau]def based
on the required Frost Accumulation Test conducted at the
intermediate compressor speed.
3.10 Test procedures for steady-state Low Temperature heating
mode tests (the H3, H32, and H31 Tests).
Except for the modifications noted in this section, conduct the
Low Temperature heating mode test using the same approach as
specified in section 3.7 for the Maximum and High Temperature tests.
After satisfying the section 3.7 requirements for the pretest
interval but before beginning to collect data to determine
Qh\k\(17) and [Edot]h\k\(17), conduct a
defrost cycle. This defrost cycle may be manually or automatically
initiated. The defrost sequence must be terminated by the action of
the heat pump's defrost controls. Begin the 30-minute data
collection interval described in section 3.7, from which
Qh\k\(17) and [Edot]h\k\(17) are determined,
no sooner than 10 minutes after defrost termination. Defrosts should
be prevented over the 30-minute data collection interval.
3.11 Additional requirements for the secondary test methods.
3.11.1 If using the Outdoor Air Enthalpy Method as the secondary
test method.
During the ``official'' test, the outdoor air-side test
apparatus described in section 2.10.1 is connected to the outdoor
unit. To help compensate for any effect that the addition of this
test apparatus may have on the unit's performance, conduct a
``preliminary'' test where the outdoor air-side test apparatus is
disconnected. Conduct a preliminary test prior to the first section
3.2 steady-state cooling mode test and prior to the first section
3.6 steady-state heating mode test. No other preliminary tests are
required so long as the unit operates the outdoor fan during all
cooling mode steady-state tests at the same speed and all heating
mode steady-state tests at the same speed. If using more than one
outdoor fan speed for the cooling mode steady-state tests, however,
conduct a preliminary test prior to each cooling mode test where a
different fan speed is first used. This same requirement applies for
the heating mode tests.
3.11.1.1 If a preliminary test precedes the official test.
a. The test conditions for the preliminary test are the same as
specified for the official test. Connect the indoor air-side test
apparatus to the indoor coil; disconnect the outdoor air-side test
apparatus. Allow the test room reconditioning apparatus and the unit
being tested to operate for at least one hour. After attaining
equilibrium conditions, measure the following quantities at equal
intervals that span 5 minutes or less:
1. The section 2.10.1 evaporator and condenser temperatures or
pressures;
2. Parameters required according to the Indoor Air Enthalpy
Method.
Continue these measurements until a 30-minute period (e.g., four
consecutive 10-minute samples) is obtained where the Table 8 or
Table 15, whichever applies, test tolerances are satisfied.
b. After collecting 30 minutes of steady-state data, reconnect
the outdoor air-side test apparatus to the unit. Adjust the exhaust
fan of the outdoor airflow measuring apparatus until averages for
the evaporator and condenser temperatures, or the saturated
temperatures corresponding to the measured pressures, agree within
0.5[emsp14][deg]F of the averages achieved when the
outdoor air-side test apparatus was disconnected. Calculate the
averages for the reconnected case using five or more consecutive
readings taken at one minute intervals. Make these consecutive
readings after re-establishing equilibrium conditions and before
initiating the official test.
3.11.1.2 If a preliminary test does not precede the official
test.
Connect the outdoor-side test apparatus to the unit. Adjust the
exhaust fan of the outdoor airflow measuring apparatus to achieve
the same external static pressure as
[[Page 69374]]
measured during the prior preliminary test conducted with the unit
operating in the same cooling or heating mode at the same outdoor
fan speed.
3.11.1.3 Official test.
a. Continue (preliminary test was conducted) or begin (no
preliminary test) the official test by making measurements for both
the Indoor and Outdoor Air Enthalpy Methods at equal intervals that
span 5 minutes or less. Discontinue these measurements only after
obtaining a 30-minute period where the specified test condition and
test operating tolerances are satisfied. To constitute a valid
official test:
(1) Achieve the energy balance specified in section 3.1.1; and,
(2) For cases where a preliminary test is conducted, the
capacities determined using the Indoor Air Enthalpy Method from the
official and preliminary test periods must agree within 2.0 percent.
b. For space cooling tests, calculate capacity from the outdoor
air-enthalpy measurements as specified in sections 7.3.3.2 and
7.3.3.3 of ASHRAE Standard 37-2009 (incorporated by reference, see
Sec. 430.3). Calculate heating capacity based on outdoor air-
enthalpy measurements as specified in sections 7.3.4.2 and 7.3.3.4.3
of the same ASHRAE Standard. Adjust the outdoor-side capacity
according to section 7.3.3.4 of ASHRAE Standard 37-2009 to account
for line losses when testing split systems. Use the outdoor unit fan
power as measured during the official test and not the value
measured during the preliminary test, as described in section 8.6.2
of ASHRAE Standard 37-2009, when calculating the capacity.
3.11.2 If using the Compressor Calibration Method as the
secondary test method.
a. Conduct separate calibration tests using a calorimeter to
determine the refrigerant flow rate. Or for cases where the
superheat of the refrigerant leaving the evaporator is less than
5[emsp14][deg]F, use the calorimeter to measure total capacity
rather than refrigerant flow rate. Conduct these calibration tests
at the same test conditions as specified for the tests in this
appendix. Operate the unit for at least one hour or until obtaining
equilibrium conditions before collecting data that will be used in
determining the average refrigerant flow rate or total capacity.
Sample the data at equal intervals that span 5 minutes or less.
Determine average flow rate or average capacity from data sampled
over a 30-minute period where the Table 8 (cooling) or the Table 15
(heating) tolerances are satisfied. Otherwise, conduct the
calibration tests according to sections 5, 6, 7, and 8 of ASHRAE
Standard 23.1-2010 (incorporated by reference, see Sec. 430.3);
sections 5, 6, 7, 8, 9, and 11 of ASHRAE Standard 41.9-2011
(incorporated by reference, see Sec. 430.3); and section 7.4 of
ASHRAE Standard 37-2009(incorporated by reference, see Sec. 430.3).
b. Calculate space cooling and space heating capacities using
the compressor calibration method measurements as specified in
section 7.4.5 and 7.4.6 respectively, of ASHRAE Standard 37-2009.
3.11.3 If using the Refrigerant-Enthalpy Method as the secondary
test method.
Conduct this secondary method according to section 7.5 of ASHRAE
Standard 37-2009. Calculate space cooling and heating capacities
using the refrigerant-enthalpy method measurements as specified in
sections 7.5.4 and 7.5.5, respectively, of the same ASHRAE Standard.
3.12 Rounding of space conditioning capacities for reporting
purposes.
a. When reporting rated capacities, round them off as specified
in Sec. 430.23 (for a single unit) and in 10 CFR 429.16 (for a
sample).
b. For the capacities used to perform the section 4
calculations, however, round only to the nearest integer.
3.13 Laboratory testing to determine off mode average power
ratings.
Conduct one of the following tests after the completion of the
B, B1, or B2 Test, whichever comes last: If
the central air conditioner or heat pump lacks a compressor
crankcase heater, perform the test in Section 3.13.1; if the central
air conditioner or heat pump has compressor crankcase heater that
lacks controls, perform the test in Section 3.13.1; if the central
air conditioner or heat pump has a compressor crankcase heater
equipped with controls, perform the test in Section 3.13.2.
3.13.1 This test determines the off mode average power rating
for central air conditioners and heat pumps that lack a compressor
crankcase heater, or have a compressor crankcase heater that lacks
controls.
a. Configure Controls: Configure the controls of the central air
conditioner or heat pump so that it operates as if connected to a
building thermostat that is set to the OFF position. This particular
test contains no requirements as to ambient conditions within the
test rooms, and room conditions are allowed to change during the
test. Ensure that the low-voltage transformer and low-voltage
components are connected.
b. Measure P1x: Determine the average power from non-zero value
data measured over a 5-minute interval of the non-operating central
air conditioner or heat pump and designate the average power as P1x,
the shoulder season total off mode power.
c. Measure Px for coil-only split systems (that would be
installed in the field with a furnace having a dedicated board for
indoor controls) and for blower-coil split systems for which a
furnace is the designated air mover: Disconnect all low-voltage
wiring for the outdoor components and outdoor controls from the low-
voltage transformer. Determine the average power from non-zero value
data measured over a 5-minute interval of the power supplied to the
(remaining) low-voltage components of the central air conditioner or
heat pump, or low-voltage power, Px.
d. Calculate P1:
Single-package systems and blower coil split systems for which
the designated air mover is not a furnace: Divide the shoulder
season total off mode power (P1x) by the number of compressors to
calculate P1, the shoulder season per-compressor off mode power. If
the compressor is a modulating-type, assign a value of 1.5 for the
number of compressors. Round P1 to the nearest watt and record as
both P1 and P2, the latter of which is the heating season per-
compressor off mode power. The expression for calculating P1 is as
follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.046
Coil-only split systems (that would be installed in the field
with a furnace having a dedicated board for indoor controls) and
blower-coil split systems for which a furnace is the designated air
mover: Subtract the low-voltage power (Px) from the shoulder season
total off mode power (P1x) and divide by the number of compressors
to calculate P1, the shoulder season per-compressor off mode power.
If the compressor is a modulating-type, assign a value of 1.5 for
the number of compressors. Round P1 to the nearest watt and record
as both P1 and P2, the latter of which is the heating season per-
compressor off mode power. The expression for calculating P1 is as
follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.047
3.13.2 This test determines the off mode average power rating
for central air conditioners and heat pumps that have a compressor
crankcase heater equipped with controls.
a. Configure Controls: Position a temperature sensor to measure
the outdoor dry-bulb temperature in the air between 2 and 6 inches
from the crankcase heater temperature sensor or, if no such
temperature sensor exists, position it in the air between 2 and 6
inches from the crankcase heater. Utilize the temperature
measurements from this sensor for this portion of the test
procedure. Configure the controls of the central air conditioner or
heat pump so that it operates as if connected to a building
thermostat that is set to the OFF position. Ensure that the low-
voltage transformer and low-voltage components are connected. Adjust
the outdoor temperature at a rate of change of no more than 20
[deg]F per hour and achieve an outdoor dry-bulb temperature of 72
[deg]F. Maintain this temperature within 2 [deg]F for at
least 5 minutes, while maintaining an indoor dry-bulb temperature of
between 75 [deg]F and 85 [deg]F.
b. Measure P1x: Determine the average power from non-zero value
data measured over a 5-minute interval of the non-operating central
air conditioner or heat pump and designate the average power as P1x,
the shoulder season total off mode power.
c. Reconfigure Controls: In the process of reaching the target
outdoor dry-bulb temperature, adjust the outdoor temperature at a
rate of change of no more than 20 [deg]F per hour. This target
temperature is the temperature specified by the manufacturer in the
DOE Compliance Certification Database at which the crankcase heater
turns on, minus five degrees Fahrenheit. Maintain this temperature
within 2 [deg]F for at least 5 minutes, while
maintaining an indoor dry-bulb temperature of between 75 [deg]F and
85 [deg]F.
d. Measure P2x: Determine the average non-zero power of the non-
operating central air conditioner or heat pump over a 5-minute
interval and designate it as P2x, the heating season total off mode
power.
[[Page 69375]]
e. Measure Px for coil-only split systems (that would be
installed in the field with a furnace having a dedicated board for
indoor controls) and for blower-coil split systems for which a
furnace is the designated air mover: Disconnect all low-voltage
wiring for the outdoor components and outdoor controls from the low-
voltage transformer. Determine the average power from non-zero value
data measured over a 5-minute interval of the power supplied to the
(remaining) low-voltage components of the central air conditioner or
heat pump, or low-voltage power, Px.
f. Calculate P1:
Single-package systems and blower coil split systems for which
the air mover is not a furnace: Divide the shoulder season total off
mode power (P1x) by the number of compressors to calculate P1, the
shoulder season per-compressor off mode power. Round to the nearest
watt. If the compressor is a modulating-type, assign a value of 1.5
for the number of compressors. The expression for calculating P1 is
as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.048
Coil-only split systems (that would be installed in the field
with a furnace having a dedicated board for indoor controls) and
blower-coil split systems for which a furnace is the designated air
mover: Subtract the low-voltage power (Px) from the shoulder season
total off mode power (P1x) and divide by the number of compressors
to calculate P1, the shoulder season per-compressor off mode power.
Round to the nearest watt. If the compressor is a modulating-type,
assign a value of 1.5 for the number of compressors. The expression
for calculating P1 is as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.049
h. Calculate P2:
Single-package systems and blower coil split systems for which
the air mover is not a furnace: Divide the heating season total off
mode power (P2x) by the number of compressors to calculate P2, the
heating season per-compressor off mode power. Round to the nearest
watt. If the compressor is a modulating-type, assign a value of 1.5
for the number of compressors. The expression for calculating P2 is
as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.050
Coil-only split systems (that would be installed in the field
with a furnace having a dedicated board for indoor controls) and
blower-coil split systems for which a furnace is the designated air
mover: Subtract the low-voltage power (Px) from the heating season
total off mode power (P2x) and divide by the number of compressors
to calculate P2, the heating season per-compressor off mode power.
Round to the nearest watt. If the compressor is a modulating-type,
assign a value of 1.5 for the number of compressors. The expression
for calculating P2 is as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.051
4. Calculations of Seasonal Performance Descriptors
4.1 Seasonal Energy Efficiency Ratio (SEER) Calculations. SEER
must be calculated as follows: For equipment covered under sections
4.1.2, 4.1.3, and 4.1.4, evaluate the seasonal energy efficiency
ratio,
[GRAPHIC] [TIFF OMITTED] TP09NO15.052
Where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.053
[[Page 69376]]
Tj = the outdoor bin temperature, [deg]F. Outdoor
temperatures are grouped or ``binned.'' Use bins of 5 [deg]F with
the 8 cooling season bin temperatures being 67, 72, 77, 82, 87, 92,
97, and 102 [deg]F.
j = the bin number. For cooling season calculations, j ranges from 1
to 8.
Additionally, for sections 4.1.2, 4.1.3, and 4.1.4, use a
building cooling load, BL(Tj). When referenced, evaluate
BL(Tj) for cooling using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.054
where,
Qc\k=2\(95) = the space cooling capacity determined from
the A2 Test and calculated as specified in section 3.3,
Btu/h.
1.1 = sizing factor, dimensionless.
The temperatures 95 [deg]F and 65 [deg]F in the building load
equation represent the selected outdoor design temperature and the
zero-load base temperature, respectively.
4.1.1 SEER calculations for an air conditioner or heat pump
having a single-speed compressor that was tested with a fixed-speed
indoor blower installed, a constant-air-volume-rate indoor blower
installed, or with no indoor blower installed.
a. Evaluate the seasonal energy efficiency ratio, expressed in
units of Btu/watt-hour, using:
SEER = PLF(0.5) * EERB
where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.055
PLF(0.5) = 1 - 0.5 [middot] CD\c\, the part-load
performance factor evaluated at a cooling load factor of 0.5,
dimensionless.
b. Refer to section 3.3 regarding the definition and calculation
of Qc(82) and [Edot]c(82).
4.1.2 SEER calculations for an air conditioner or heat pump
having a single-speed compressor and a variable-speed variable-air-
volume-rate indoor blower.
4.1.2.1 Units covered by section 3.2.2.1 where indoor blower
capacity modulation correlates with the outdoor dry bulb
temperature. The manufacturer must provide information on how the
indoor air volume rate or the indoor blower speed varies over the
outdoor temperature range of 67 [deg]F to 102 [deg]F. Calculate SEER
using Equation 4.1-1. Evaluate the quantity
qc(Tj)/N in Equation 4.1-1 using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.056
[GRAPHIC] [TIFF OMITTED] TP09NO15.057
where,
Qc(Tj) = the space cooling capacity of the
test unit when operating at outdoor temperature, Tj, Btu/
h.
nj/N = fractional bin hours for the cooling season; the
ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless.
a. For the space cooling season, assign nj/N as
specified in Table 18. Use Equation 4.1-2 to calculate the building
load, BL(Tj). Evaluate Qc(Tj)
using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.058
the space cooling capacity of the test unit at outdoor temperature
Tj if operated at the Cooling Minimum Air Volume Rate,
Btu/h.
[[Page 69377]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.059
the space cooling capacity of the test unit at outdoor temperature
Tj if operated at the Cooling Full-load Air Volume Rate,
Btu/h.
b. For units where indoor blower speed is the primary control
variable, FPc\k=1\ denotes the fan speed used during the
required A1 and B1 Tests (see section
3.2.2.1), FPc\k=2\ denotes the fan speed used during the
required A2 and B2 Tests, and
FPc(Tj) denotes the fan speed used by the unit
when the outdoor temperature equals Tj. For units where
indoor air volume rate is the primary control variable, the three
FPc's are similarly defined only now being expressed in
terms of air volume rates rather than fan speeds. Refer to sections
3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 regarding the definitions and
calculations of Qc\k=1\(82),
Qc\k=1\(95),Qc\k=2\(82), and
Qc\k=2\(95).
[GRAPHIC] [TIFF OMITTED] TP09NO15.060
where,
PLFj = 1 - CD\c\ [middot] [1 -
X(Tj)], the part load factor, dimensionless.
[Edot]c(Tj) = the electrical power consumption
of the test unit when operating at outdoor temperature
Tj, W.
c. The quantities X(Tj) and nj/N are the
same quantities as used in Equation 4.1.2-1.
d. Evaluate [Edot]c(Tj) using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.061
the electrical power consumption of the test unit at outdoor
temperature Tj if operated at the Cooling Minimum Air
Volume Rate, W.
[GRAPHIC] [TIFF OMITTED] TP09NO15.062
e. The parameters FPc\k=1\, and FPc\k=2\,
and FPc(Tj) are the same quantities that are
used when evaluating Equation 4.1.2-2. Refer to sections 3.2.2.1,
3.1.4 to 3.1.4.2, and 3.3 regarding the definitions and calculations
of [Edot]c\k=1\(82), [Edot]c\k=1\(95),
[Edot]c\k=2\(82), and [Edot]c\k=2\(95).
4.1.2.2 Units covered by section 3.2.2.2 where indoor blower
capacity modulation is used to adjust the sensible to total cooling
capacity ratio. Calculate SEER as specified in section 4.1.1.
4.1.3 SEER calculations for an air conditioner or heat pump
having a two-capacity compressor. Calculate SEER using Equation 4.1-
1. Evaluate the space cooling capacity, Qc\k=1\
(Tj), and electrical power consumption,
[Edot]c\k=1\ (Tj), of the test unit when
operating at low compressor capacity and outdoor temperature
Tj using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.063
where Qc\k=1\ (82) and [Edot]c\k=1\ (82) are
determined from the B1 Test, Qc\k=1\ (67) and
[Edot]c\k=1\ (67) are determined from the
F1Test, and all four quantities are calculated as
specified in section 3.3. Evaluate the space cooling capacity,
Qc\k=2\ (Tj), and electrical power
consumption, [Edot]c\k=2\ (Tj), of the test
unit when operating at high compressor capacity and outdoor
temperature Tj using,
[[Page 69378]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.064
where Qc\k=2\(95) and [Edot]c\k=2\(95) are
determined from the A2 Test, Qc\k=2\(82), and
[Edot]c\k=2\(82), are determined from the
B2Test, and all are calculated as specified in section
3.3.
The calculation of Equation 4.1-1 quantities
qc(Tj)/N and ec(Tj)/N
differs depending on whether the test unit would operate at low
capacity (section 4.1.3.1), cycle between low and high capacity
(section 4.1.3.2), or operate at high capacity (sections 4.1.3.3 and
4.1.3.4) in responding to the building load. For units that lock out
low capacity operation at higher outdoor temperatures, the
manufacturer must supply information regarding this temperature so
that the appropriate equations are used. Use Equation 4.1-2 to
calculate the building load, BL(Tj), for each temperature
bin.
4.1.3.1 Steady-state space cooling capacity at low compressor
capacity is greater than or equal to the building cooling load at
temperature Tj, Qc\k=1\(Tj) >=
BL(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.065
where,
Xk=1(Tj) = BL(Tj)/
Qck=1 (Tj), the cooling mode low
capacity load factor for temperature bin j, dimensionless.
PLFj = 1 - CDc [middot] [1 -
Xk=1(Tj)], the part load factor,
dimensionless.
[GRAPHIC] [TIFF OMITTED] TP09NO15.066
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 18. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qck=1(Tj)
and [Edot]ck=1(Tj).
Table 18--Distribution of Fractional Hours Within Cooling Season Temperature Bins
----------------------------------------------------------------------------------------------------------------
Representative Fraction of total
Bin number, j Bin temperature temperature for temperature bin
range [deg]F bin [deg]F hours, nj/N
----------------------------------------------------------------------------------------------------------------
1...................................................... 65-69 67 0.214
2...................................................... 70-74 72 0.231
3...................................................... 75-79 77 0.216
4...................................................... 80-84 82 0.161
5...................................................... 85-89 87 0.104
6...................................................... 90-94 92 0.052
7...................................................... 95-99 97 0.018
8...................................................... 100-104 102 0.004
----------------------------------------------------------------------------------------------------------------
4.1.3.2 Unit alternates between high (k=2) and low (k=1)
compressor capacity to satisfy the building cooling load at
temperature Tj,
Qck=1(Tj) j)
ck=2(Tj).
[[Page 69379]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.067
where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.068
Xk=2(Tj) = 1 - Xk=1(Tj),
the cooling mode, high capacity load factor for temperature bin j,
dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 18. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qck=1(Tj)
and [Edot]ck=1(Tj). Use Equations
4.1.3-3 and 4.1.3-4, respectively, to evaluate
Qck=2(Tj) and
[Edot]ck=2(Tj).
4.1.3.3 Unit only operates at high (k=2) compressor capacity at
temperature Tj and its capacity is greater than the
building cooling load, BL(Tj) <
Qck=2(Tj). This section applies to
units that lock out low compressor capacity operation at higher
outdoor temperatures.
[GRAPHIC] [TIFF OMITTED] TP09NO15.069
where,
Xk=2(Tj) = BL(Tj)/
Qck=2(Tj), the cooling mode high
capacity load factor for temperature bin j, dimensionless.
PLFj = 1 - CDc(k = 2) * [1 - Xk=2(Tj) the part load factor,
dimensionless.
[GRAPHIC] [TIFF OMITTED] TP09NO15.070
4.1.3.4 Unit must operate continuously at high (k=2) compressor
capacity at temperature Tj, BL(Tj) >=
Qck=2(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.071
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 18. Use Equations 4.1.3-3 and 4.1.3-4,
respectively, to evaluate Qck=2(Tj)
and [Edot]ck=2(Tj).
4.1.4 SEER calculations for an air conditioner or heat pump
having a variable-speed compressor. Calculate SEER using Equation
4.1-1. Evaluate the space cooling capacity,
Qck=1(Tj), and electrical power
consumption, [Edot]ck=1(Tj), of the
test unit when operating at minimum compressor speed and outdoor
temperature Tj. Use,
[GRAPHIC] [TIFF OMITTED] TP09NO15.072
[[Page 69380]]
where Qck=1(82) and
[Edot]ck=1(82) are determined from the
B1 Test, Qck=1(67) and
[Edot]ck=1(67) are determined from the F1
Test, and all four quantities are calculated as specified in section
3.3. Evaluate the space cooling capacity,
Qck=2(Tj), and electrical power
consumption, [Edot]ck=2(Tj), of the
test unit when operating at maximum compressor speed and outdoor
temperature Tj. Use Equations 4.1.3-3 and 4.1.3-4,
respectively, where Qck=2(95) and
[Edot]ck=2(95) are determined from the
A2 Test, Qck=2(82) and
[Edot]ck=2(82) are determined from the
B2 Test, and all four quantities are calculated as
specified in section 3.3. Calculate the space cooling capacity,
Qck=v(Tj), and electrical power
consumption, [Edot]ck=v(Tj), of the
test unit when operating at outdoor temperature Tj and
the intermediate compressor speed used during the section 3.2.4 (and
Table 7) EV Test using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.073
4.1.4.1 Steady-state space cooling capacity when operating at
minimum compressor speed is greater than or equal to the building
cooling load at temperature Tj,
Qck=1(Tj) >= BL(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.074
where,
Xk=1(Tj) = BL(Tj)/
Qck=1(Tj), the cooling mode minimum
speed load factor for temperature bin j, dimensionless.
PLFj = 1 - CDc [middot] [1 -
Xk=1(Tj)], the part load factor,
dimensionless.
nj/N = fractional bin hours for the cooling season; the
ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 18. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qck=1
(Tj) and [Edot]ck=1
(Tj).
4.1.4.2 Unit operates at an intermediate compressor speed (k=i)
in order to match the building cooling load at temperature
Tj,Qck=1(Tj) <
BL(Tj) < Qck=2(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.075
where,
Qck=i(Tj) = BL(Tj), the
space cooling capacity delivered by the unit in matching the
building load at temperature Tj, Btu/h. The matching
occurs with the unit operating at compressor speed k = i.
[GRAPHIC] [TIFF OMITTED] TP09NO15.076
the electrical power input required by the test unit when operating
at a compressor speed of k = i and temperature Tj, W.
EERk=i(Tj) = the steady-state energy
efficiency ratio of the test unit when operating at a compressor
speed of k = i and temperature Tj, Btu/h per W.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 18. For each temperature bin where the
unit operates at an intermediate compressor speed, determine the
energy efficiency ratio EERk=i(Tj) using,
EERk=i(Tj) = A + B [middot] Tj + C
[middot] Tj\2\.
For each unit, determine the coefficients A, B, and C by
conducting the following calculations once:
[GRAPHIC] [TIFF OMITTED] TP09NO15.077
[[Page 69381]]
where,
T1 = the outdoor temperature at which the unit, when
operating at minimum compressor speed, provides a space cooling
capacity that is equal to the building load
(Qck=1 (Tl) = BL(T1)),
[deg]F. Determine T1 by equating Equations 4.1.3-1 and
4.1-2 and solving for outdoor temperature.
Tv = the outdoor temperature at which the unit, when
operating at the intermediate compressor speed used during the
section 3.2.4 EV Test, provides a space cooling capacity
that is equal to the building load (Qck=v
(Tv) = BL(Tv)), [deg]F. Determine
Tv by equating Equations 4.1.4-1 and 4.1-2 and solving
for outdoor temperature.
T2 = the outdoor temperature at which the unit, when
operating at maximum compressor speed, provides a space cooling
capacity that is equal to the building load
(Qck=2 (T2) = BL(T2)),
[deg]F. Determine T2 by equating Equations 4.1.3-3 and
4.1-2 and solving for outdoor temperature.
[GRAPHIC] [TIFF OMITTED] TP09NO15.078
4.1.4.3 Unit must operate continuously at maximum (k=2)
compressor speed at temperature Tj, BL(Tj)
>=Qck=2(Tj). Evaluate the Equation
4.1-1 quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.079
as specified in section 4.1.3.4 with the understanding that
Qck=2(Tj) and
[Edot]ck=2(Tj) correspond to
maximum compressor speed operation and are derived from the results
of the tests specified in section 3.2.4.
4.1.5 SEER calculations for an air conditioner or heat pump
having a single indoor unit with multiple blowers. Calculate SEER
using Eq. 4.1-1, where qc(Tj)/N and ec(Tj)/N
are evaluated as specified in applicable below subsection.
4.1.5.1 For multiple blower systems that are connected to a
lone, single-speed outdoor unit. a. Calculate the space cooling
capacity, Qk=1(Tj), and electrical power consumption,
[Edot]k=1(Tj), of the test unit when operating at the
cooling minimum air volume rate and outdoor temperature
Tj using the equations given in section 4.1.2.1.
Calculate the space cooling capacity, Qk=2(Tj), and
electrical power consumption, [Edot]k=2(Tj), of the test
unit when operating at the cooling full-load air volume rate and
outdoor temperature Tj using the equations given in
section 4.1.2.1. In evaluating the section 4.1.2.1 equations,
determine the quantities Qk=1(82) and
[Edot]k=1(82) from the B1 Test, Qk=1(95) and
[Edot]k=1(82) from the Al Test, Qk=2(82) and
[Edot]k=2(82) from the B2 Test, and Qk=2(95)
and [Edot]k=2(95) from the A2 Test. Evaluate all eight
quantities as specified in section 3.3. Refer to section 3.2.2.1 and
Table 5 for additional information on the four referenced laboratory
tests. b. Determine the cooling mode cyclic degradation coefficient,
CDc, as per sections 3.2.2.1 and 3.5 to 3.5.3. Assign
this same value to CDc(K=2). c. Except for using the
above values of Qk=1(Tj), [Edot]k=1(Tj),
[Edot]k=2(Tj), Qk=2(Tj), CDc, and
CDc (K=2), calculate the quantities
qc(Tj)/N and ec(Tj)/N as
specified in section 4.1.3.1 for cases where Qk=1(Tj) >=
BL(Tj). For all other outdoor bin temperatures,
Tj, calculate qc(Tj)/N and ec(Tj)/N
as specified in section 4.1.3.3 if Qk=2(Tj) > BL
(Tj) or as specified in section 4.1.3.4 if
Qk=2(Tj) <= BL(Tj).
4.1.5.2 For multiple blower systems that are connected to either
a lone outdoor unit having a two-capacity compressor or to two
separate but identical model single-speed outdoor units. Calculate
the quantities qc(Tj)/N and ec(Tj)/N as
specified in section 4.1.3.
4.2 Heating Seasonal Performance Factor (HSPF) Calculations.
Unless an approved alternative efficiency determination method is
used, as set forth in 10 CFR 429.70(e), HSPF must be calculated as
follows: Six generalized climatic regions are depicted in Figure 1
and otherwise defined in Table 19. For each of these regions and for
each applicable standardized design heating requirement, evaluate
the heating seasonal performance factor using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.080
Where,
eh(Tj)/N = The ratio of the electrical energy
consumed by the heat pump during periods of the space heating season
when the outdoor temperature fell within the range represented by
bin temperature Tj to the total number of hours in the
heating season (N), W. For heat pumps having a heat comfort
controller, this ratio may also include electrical energy used by
resistive elements to maintain a minimum air delivery temperature
(see 4.2.5).
RH(Tj)/N = The ratio of the electrical energy used for
resistive space heating during periods when the outdoor temperature
fell within the range represented by bin temperature Tj
to the total number of hours in the heating season (N), W. Except as
noted in section 4.2.5, resistive space heating is modeled as being
used to meet that portion of the building load that the heat pump
does not meet because of insufficient capacity or because the heat
pump automatically turns off at the lowest outdoor temperatures. For
heat pumps having a heat comfort controller, all or part of the
electrical energy used by resistive
[[Page 69382]]
heaters at a particular bin temperature may be reflected in
eh(Tj)/N (see 4.2.5).
Tj = the outdoor bin temperature, [deg]F. Outdoor
temperatures are ``binned'' such that calculations are only
performed based one temperature within the bin. Bins of 5 [deg]F are
used.
nj/N = Fractional bin hours for the heating season; the
ratio of the number of hours during the heating season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
heating season, dimensionless. Obtain nj/N values from
Table 19.
j = the bin number, dimensionless.
J = for each generalized climatic region, the total number of
temperature bins, dimensionless. Referring to Table 19, J is the
highest bin number (j) having a nonzero entry for the fractional bin
hours for the generalized climatic region of interest.
Fdef = the demand defrost credit described in section
3.9.2, dimensionless.
BL(Tj) = the building space conditioning load
corresponding to an outdoor temperature of Tj; the
heating season building load also depends on the generalized
climatic region's outdoor design temperature and the design heating
requirement, Btu/h.
Table 19--Generalized Climatic Region Information
--------------------------------------------------------------------------------------------------------------------------------------------------------
Region Number I II III IV V VI
--------------------------------------------------------------------------------------------------------------------------------------------------------
Heating Load Hours, HLH................................. 750 1250 1750 2250 2750 * 2750
Outdoor Design Temperature, TOD......................... 37 27 17 5 -10 30
-----------------------------------------------------------------------------------------------
j Tj ([deg]F)........................................... Fractional Bin Hours, nj/N
1 62.................................................... .291 .215 .153 .132 .106 .113
-----------------------------------------------------------------------------------------------
2 57.................................................... .239 .189 .142 .111 .092 .206
3 52.................................................... .194 .163 .138 .103 .086 .215
4 47.................................................... .129 .143 .137 .093 .076 .204
5 42.................................................... .081 .112 .135 .100 .078 .141
6 37.................................................... .041 .088 .118 .109 .087 .076
7 32.................................................... .019 .056 .092 .126 .102 .034
8 27.................................................... .005 .024 .047 .087 .094 .008
9 22.................................................... .001 .008 .021 .055 .074 .003
10 17................................................... 0 .002 .009 .036 .055 0
11 12................................................... 0 0 .005 .026 .047 0
12 7.................................................... 0 0 .002 .013 .038 0
13 2.................................................... 0 0 .001 .006 .029 0
14 -3................................................... 0 0 0 .002 .018 0
15 -8................................................... 0 0 0 .001 .010 0
16 -13.................................................. 0 0 0 0 .005 0
17 -18.................................................. 0 0 0 0 .002 0
18 -23.................................................. 0 0 0 0 .001 0
--------------------------------------------------------------------------------------------------------------------------------------------------------
* Pacific Coast Region.
Evaluate the building heating load using
[GRAPHIC] [TIFF OMITTED] TP09NO15.081
Where,
TOD = the outdoor design temperature, [deg]F. An outdoor
design temperature is specified for each generalized climatic region
in Table 19.
C = 0.77, a correction factor which tends to improve the agreement
between calculated and measured building loads, dimensionless.
DHR = the design heating requirement (see section 1.2, Definitions),
Btu/h.
Calculate the minimum and maximum design heating requirements
for each generalized climatic region as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.082
[[Page 69383]]
Where Qhk(47) is expressed in units of Btu/h
and otherwise defined as follows:
1. For a single-speed heat pump tested as per section 3.6.1,
Qhk(47) = Qh(47), the space heating
capacity determined from the H1 Test.
2. For a variable-speed heat pump, a section 3.6.2 single-speed
heat pump, or a two-capacity heat pump not covered by item 3,
Qnk(47) = Qnk=2(47), the
space heating capacity determined from the H12 Test.
3. For two-capacity, northern heat pumps (see section 1.2,
Definitions), Qkh(47) =
Qk=1h(47), the space heating capacity
determined from the H11 Test.
If the optional H1N Test is conducted on a variable-
speed heat pump, the manufacturer has the option of defining
Q\k\h(47) as specified above in item 2 or as
Q\k\h(47)=Q\k=N\h(47), the space heating
capacity determined from the H1N Test.
For all heat pumps, HSPF accounts for the heating delivered and
the energy consumed by auxiliary resistive elements when operating
below the balance point. This condition occurs when the building
load exceeds the space heating capacity of the heat pump condenser.
For HSPF calculations for all heat pumps, see either section 4.2.1,
4.2.2, 4.2.3, or 4.2.4, whichever applies.
For heat pumps with heat comfort controllers (see section 1.2,
Definitions), HSPF also accounts for resistive heating contributed
when operating above the heat-pump-plus-comfort-controller balance
point as a result of maintaining a minimum supply temperature. For
heat pumps having a heat comfort controller, see section 4.2.5 for
the additional steps required for calculating the HSPF.
Table 20--Standardized Design Heating Requirements (Btu/h)
------------------------------------------------------------------------
------------------------------------------------------------------------
5,000................................... 25,000 50,000 90,000
10,000................................... 30,000 60,000 100,000
15,000................................... 35,000 70,000 110,000
20,000................................... 40,000 80,000 130,000
------------------------------------------------------------------------
4.2.1 Additional steps for calculating the HSPF of a heat pump
having a single-speed compressor that was tested with a fixed-speed
indoor blower installed, a constant-air-volume-rate indoor blower
installed, or with no indoor blower installed.
[GRAPHIC] [TIFF OMITTED] TP09NO15.083
where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.084
whichever is less; the heating mode load factor for temperature bin
j, dimensionless.
Qh(Tj) = the space heating capacity of the
heat pump when operating at outdoor temperature Tj, Btu/
h.
[Edot]h(Tj) = the electrical power consumption
of the heat pump when operating at outdoor temperature
Tj, W.
[delta](Tj) = the heat pump low temperature cut-out
factor, dimensionless.
PLFj = 1 - [Cdot]D\h\ [middot] [1 -
X(Tj)] the part load factor, dimensionless.
Use Equation 4.2-2 to determine BL(Tj). Obtain
fractional bin hours for the heating season, nj/N, from
Table 19.
Determine the low temperature cut-out factor using
[GRAPHIC] [TIFF OMITTED] TP09NO15.085
where,
Toff = the outdoor temperature when the compressor is
automatically shut off, [deg]F. (If no such temperature exists,
Tj is always greater than Toff and
Ton).
Ton = the outdoor temperature when the compressor is
automatically turned back on, if applicable, following an automatic
shut-off, [deg]F.
Calculate Qh(Tj) and
[Edot]h(Tj) using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.086
[[Page 69384]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.087
where Qh(47) and [Edot]h(47) are determined
from the H1 Test and calculated as specified in section 3.7;
Qh(35) and [Edot]h(35) are determined from the
H2 Test and calculated as specified in section 3.9.1; and
Qh(17) and [Edot]h(17) are determined from the
H3 Test and calculated as specified in section 3.10.
4.2.2 Additional steps for calculating the HSPF of a heat pump
having a single-speed compressor and a variable-speed, variable-air-
volume-rate indoor blower. The manufacturer must provide information
about how the indoor air volume rate or the indoor blower speed
varies over the outdoor temperature range of 65[deg]F to -23[deg]F.
Calculate the quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.088
in Equation 4.2-1 as specified in section 4.2.1 with the
exception of replacing references to the H1C Test and section 3.6.1
with the H1C1 Test and section 3.6.2. In addition,
evaluate the space heating capacity and electrical power consumption
of the heat pump Qh(Tj) and
[Edot]h(Tj) using
[GRAPHIC] [TIFF OMITTED] TP09NO15.089
where the space heating capacity and electrical power consumption at
both low capacity (k=1) and high capacity (k=2) at outdoor
temperature Tj are determined using
[GRAPHIC] [TIFF OMITTED] TP09NO15.090
For units where indoor blower speed is the primary control
variable, FPh\k=1\ denotes the fan speed used during the
required H11 and H31 Tests (see Table 11),
FPh\k=2\ denotes the fan speed used during the required
H12, H22, and H32 Tests, and
FPh(Tj) denotes the fan speed used by the unit
when the outdoor temperature equals Tj. For units where
indoor air volume rate is the primary control variable, the three
FPh's are similarly defined only now being expressed in
terms of air volume rates rather than fan speeds. Determine
Qh\k=1\(47) and [Edot]h\k=1\(47) from the
H11 Test, and Qh\k=2\(47) and
[Edot]h\k=2\(47) from the H12 Test. Calculate
all four quantities as specified in section 3.7. Determine
Qh\k=1\(35) and [Edot]h\k=1\(35) as specified
in section 3.6.2; determine Qh\k=2\(35) and
[Edot]h\k=2\(35) and from the H22 Test and the
calculation specified in section 3.9. Determine
Qh\k=1\(17) and [Edot]h\k=1\(17 from the
H31 Test, and Qh\k=2\(17) and
[Edot]h\k=2\(17) from the H32 Test. Calculate
all four quantities as specified in section 3.10.
4.2.3 Additional steps for calculating the HSPF of a heat pump
having a two-capacity compressor. The calculation of the Equation
4.2-1 quantities differ depending upon
[[Page 69385]]
whether the heat pump would operate at low capacity (section
4.2.3.1), cycle between low and high capacity (Section 4.2.3.2), or
operate at high capacity (sections 4.2.3.3 and 4.2.3.4) in
responding to the building load. For heat pumps that lock out low
capacity operation at low outdoor temperatures, the manufacturer
must supply information regarding the cutoff temperature(s) so that
the appropriate equations can be selected.
[GRAPHIC] [TIFF OMITTED] TP09NO15.091
a. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at low compressor
capacity and outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TP09NO15.092
b. Evaluate the space heating capacity and electrical power
consumption (Qh\k=2\(Tj) and
[Edot]h\k=2\ (Tj)) of the heat pump when
operating at high compressor capacity and outdoor temperature Tj by
solving Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2.
Determine Qh\k=1\(62) and [Edot]h\k=1\(62)
from the H01 Test, Qh\k=1\(47) and
[Edot]h\k=1\(47) from the H11 Test, and
Qh\k=2\(47) and [Edot]h\k=2\(47) from the
H12 Test. Calculate all six quantities as specified in
section 3.7. Determine Qh\k=2\(35) and
[Edot]h\k=2\(35) from the H22 Test and, if
required as described in section 3.6.3, determine
Qh\k=1\(35) and [Edot]h\k=1\(35) from the
H21 Test. Calculate the required 35[deg]F quantities as
specified in section 3.9. Determine Qh\k=2\(17) and
[Edot]h\k=2\(17) from the H32 Test and, if
required as described in section 3.6.3, determine
Qh\k=1\(17) and [Edot]h\k=1\(17) from the
H31 Test. Calculate the required 17[emsp14][deg]F
quantities as specified in section 3.10.
4.2.3.1 Steady-state space heating capacity when operating at
low compressor capacity is greater than or equal to the building
heating load at temperature Tj,
Qhk=1(Tj) >=BL(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.093
Where,
Xk=1(Tj) = BL(Tj) /
Qhk=1(Tj), the heating mode low
capacity load factor for temperature bin j, dimensionless.
PLFj = 1-CDh [middot] [ 1-
Xk=1(Tj)], the part load factor,
dimensionless.
[delta]'(Tj) = the low temperature cutoff factor,
dimensionless.
Determine the low temperature cut-out factor using
[GRAPHIC] [TIFF OMITTED] TP09NO15.094
Where Toff and Ton are defined in section
4.2.1. Use the calculations given in section 4.2.3.3, and not the
above, if:
(a) The heat pump locks out low capacity operation at low
outdoor temperatures and
(b) Tj is below this lockout threshold temperature.
4.2.3.2 Heat pump alternates between high (k=2) and low (k=1)
compressor capacity to satisfy the building heating load
[[Page 69386]]
at a temperature Tj,
Qhk=1(Tj) j)
hk=2(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.095
Where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.096
Xk=2(Tj) = 1-Xk=1(Tj)
the heating mode, high capacity load factor for temperature bin
j, dimensionless.
Determine the low temperature cut-out factor,
[delta]'(Tj), using Equation 4.2.3-3.
4.2.3.3 Heat pump only operates at high (k=2) compressor
capacity at temperature Tj and its capacity is greater
than the building heating load, BL(Tj)
hk=2(Tj). This section applies to
units that lock out low compressor capacity operation at low outdoor
temperatures.
[GRAPHIC] [TIFF OMITTED] TP09NO15.097
Where,
Xk=2(Tj) = BL(Tj)/
Qhk=2(Tj). PLFj = 1-
CDh(k = 2) * [1-Xk=2(Tj)
If the H1C2 Test described in section 3.6.3 and Table
12 is not conducted, set CDh (k=2) equal to
the default value specified in section 3.8.1.
Determine the low temperature cut-out factor,
[delta](Tj), using Equation 4.2.3-3.
4.2.3.4 Heat pump must operate continuously at high (k=2)
compressor capacity at temperature Tj, BL(Tj)
>= Qhk=2(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.098
Where
[GRAPHIC] [TIFF OMITTED] TP09NO15.099
4.2.4 Additional steps for calculating the HSPF of a heat pump
having a variable-speed compressor. Calculate HSPF using Equation
4.2-1. Evaluate the space heating capacity,
Qhk=1(Tj), and electrical power
consumption, [Edot]hk=1(Tj), of the
heat pump when operating at minimum compressor speed and outdoor
temperature Tj using
[[Page 69387]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.100
Where Qhk=1(62) and
[Edot]hk=1(62) are determined from the
H01 Test, Qhk=1(47) and
[Edot]hk=1(47) are determined from the
H11Test, and all four quantities are calculated as
specified in section 3.7. Evaluate the space heating capacity,
Qhk=2(Tj), and electrical power
consumption, [Edot]hk=2(Tj), of the
heat pump when operating at maximum compressor speed and outdoor
temperature Tj by solving Equations 4.2.2-3 and 4.2.2-4,
respectively, for k=2. Determine the Equation 4.2.2-3 and 4.2.2-4
quantities Qhk=2(47) and
[Edot]hk=2(47) from the H12 Test
and the calculations specified in section 3.7. Determine
Qhk=2(35) and
[Edot]hk=2(35) from the H22 Test
and the calculations specified in section 3.9 or, if the
H22 Test is not conducted, by conducting the calculations
specified in section 3.6.4. Determine
Qhk=2(17) and
[Edot]hk=2(17) from the H32 Test
and the calculations specified in section 3.10. Calculate the space
heating capacity, Qhk=v(Tj), and
electrical power consumption,
[Edot]hk=v(Tj), of the heat pump
when operating at outdoor temperature Tj and the
intermediate compressor speed used during the section 3.6.4
H2V Test using
[GRAPHIC] [TIFF OMITTED] TP09NO15.101
Where Qhk=v(35) and
[Edot]hk=v(35) are determined from the
H2V Test and calculated as specified in section 3.9.
Approximate the slopes of the k=v intermediate speed heating
capacity and electrical power input curves, MQ and
ME, as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.102
4.2.4.1 Steady-state space heating capacity when operating at
minimum compressor speed is greater than or equal to the building
heating load at temperature Tj,
Qhk=1(Tj >= BL(Tj).
Evaluate the Equation 4.2-1 quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.103
[[Page 69388]]
as specified in section 4.2.3.1. Except now use Equations 4.2.4-1
and 4.2.4-2 to evaluate Qhk=1(Tj)
and [Edot]hk=1(Tj), respectively,
and replace section 4.2.3.1 references to ``low capacity'' and
section 3.6.3 with ``minimum speed'' and section 3.6.4. Also, the
last sentence of section 4.2.3.1 does not apply.
4.2.4.2 Heat pump operates at an intermediate compressor speed
(k=i) in order to match the building heating load at a temperature
Tj, Qhk=1(Tj)
j) hk=2(Tj).
Calculate
[GRAPHIC] [TIFF OMITTED] TP09NO15.104
and [delta](Tj) is evaluated using Equation 4.2.3-3
while,
Qhk=i(Tj) = BL(Tj), the
space heating capacity delivered by the unit in matching the
building load at temperature (Tj), Btu/h. The matching
occurs with the heat pump operating at compressor speed k=i.
COPk=i(Tj) = the steady-state coefficient of
performance of the heat pump when operating at compressor speed k=i
and temperature Tj, dimensionless.
For each temperature bin where the heat pump operates at an
intermediate compressor speed, determine
COPk=i(Tj) using,
COPk=i(Tj) = A + B . Tj + C .
Tj2.
For each heat pump, determine the coefficients A, B, and C by
conducting the following calculations once:
[GRAPHIC] [TIFF OMITTED] TP09NO15.105
Where,=
T3 = the outdoor temperature at which the heat pump, when
operating at minimum compressor speed, provides a space heating
capacity that is equal to the building load
(Qhk=1(T3) = BL(T3)),
[deg]F. Determine T3 by equating Equations 4.2.4-1 and
4.2-2 and solving for:
[GRAPHIC] [TIFF OMITTED] TP09NO15.106
outdoor temperature.
Tvh = the outdoor temperature at which the heat pump,
when operating at the intermediate compressor speed used during the
section 3.6.4 H2V Test, provides a space heating capacity
that is equal to the building load
(Qhk=v(Tvh) = BL(Tvh)),
[deg]F. Determine Tvh by equating Equations 4.2.4-3 and
4.2-2 and solving for outdoor temperature.
T4 = the outdoor temperature at which the heat pump, when
operating at maximum compressor speed, provides a space heating
capacity that is equal to the building load
(Qhk=2(T4) = BL(T4)),
[deg]F. Determine T4 by equating Equations 4.2.2-3 (k=2)
and 4.2-2 and solving for outdoor temperature.
[GRAPHIC] [TIFF OMITTED] TP09NO15.107
[[Page 69389]]
For multiple-split heat pumps (only), the following procedures
supersede the above requirements for calculating
COPhk=i(Tj). For each temperature
bin where T3 > Tj > Tvh,
[GRAPHIC] [TIFF OMITTED] TP09NO15.108
4.2.4.3 Heat pump must operate continuously at maximum (k=2)
compressor speed at temperature Tj, BL(Tj) >=
Qhk=2(Tj). Evaluate the Equation
4.2-1 quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.109
as specified in section 4.2.3.4 with the understanding that
Qhk=2(Tj) and
[Edot]hk=2(Tj) correspond to
maximum compressor speed operation and are derived from the results
of the specified section 3.6.4 tests.
4.2.5 Heat pumps having a heat comfort controller. Heat pumps
having heat comfort controllers, when set to maintain a typical
minimum air delivery temperature, will cause the heat pump condenser
to operate less because of a greater contribution from the resistive
elements. With a conventional heat pump, resistive heating is only
initiated if the heat pump condenser cannot meet the building load
(i.e., is delayed until a second stage call from the indoor
thermostat). With a heat comfort controller, resistive heating can
occur even though the heat pump condenser has adequate capacity to
meet the building load (i.e., both on during a first stage call from
the indoor thermostat). As a result, the outdoor temperature where
the heat pump compressor no longer cycles (i.e., starts to run
continuously), will be lower than if the heat pump did not have the
heat comfort controller.
4.2.5.1 Heat pump having a heat comfort controller: additional
steps for calculating the HSPF of a heat pump having a single-speed
compressor that was tested with a fixed-speed indoor blower
installed, a constant-air-volume-rate indoor blower installed, or
with no indoor blower installed. Calculate the space heating
capacity and electrical power of the heat pump without the heat
comfort controller being active as specified in section 4.2.1
(Equations 4.2.1-4 and 4.2.1-5) for each outdoor bin temperature,
Tj, that is listed in Table 19. Denote these capacities
and electrical powers by using the subscript ``hp'' instead of
``h.'' Calculate the mass flow rate (expressed in pounds-mass of dry
air per hour) and the specific heat of the indoor air (expressed in
Btu/lbmda [middot] [deg]F) from the results of the H1
Test using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.110
where Vis, Vimx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 19, calculate
the nominal temperature of the air leaving the heat pump condenser
coil using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.111
Evaluate eh(Tj/N), RH(Tj)/N,
X(Tj), PLFj, and [delta](Tj) as
specified in section 4.2.1. For each bin calculation, use the space
heating capacity and electrical power from Case 1 or Case 2,
whichever applies.
Case 1. For outdoor bin temperatures where
To(Tj) is equal to or greater than
TCC (the maximum supply temperature determined according
to section 3.1.9), determine Qh(Tj) and
[Edot]h(Tj) as specified in section 4.2.1
(i.e., Qh(Tj) = Qhp(Tj)
and [Edot]hp(Tj) =
[Edot]hp(Tj)). Note: Even though
To(Tj) >= Tcc, resistive heating
may be required; evaluate Equation 4.2.1-2 for all bins.
Case 2. For outdoor bin temperatures where
To(Tj) >Tcc, determine
Qh(Tj) and [Edot]h(Tj)
using,
Qh(Tj) = Qhp(Tj) + QCC(Tj)
[Edot]h(Tj) = [Edot]hp(Tj) + [Edot]CC(Tj)
Where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.112
Note: Even though To(Tj) < Tcc,
additional resistive heating may be required; evaluate Equation
4.2.1-2 for all bins.
4.2.5.2 Heat pump having a heat comfort controller: additional
steps for calculating the HSPF of a heat pump having a single-speed
compressor and a variable-speed, variable-air-volume-rate indoor
blower. Calculate the space heating capacity and electrical power of
the heat pump without the heat comfort controller being active as
specified in section 4.2.2 (Equations 4.2.2-1 and 4.2.2-2) for each
outdoor bin temperature, Tj, that is listed in Table 19.
Denote these capacities and electrical powers by using the subscript
``hp'' instead of ``h.'' Calculate the mass flow rate (expressed in
pounds-mass of dry air per hour) and the specific heat of the indoor
air
[[Page 69390]]
(expressed in Btu/lbmda [middot] [deg]F) from the results
of the H12 Test using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.113
Where Vis, Vimx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 19, calculate
the nominal temperature of the air leaving the heat pump condenser
coil using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.114
Evaluate eh(Tj)/N, RH(Tj)/N,
X(Tj), PLFj, and [delta](Tj) as
specified in section 4.2.1 with the exception of replacing
references to the H1C Test and section 3.6.1 with the
H1C1 Test and section 3.6.2. For each bin calculation,
use the space heating capacity and electrical power from Case 1 or
Case 2, whichever applies.
Case 1. For outdoor bin temperatures where
To(Tj) is equal to or greater than
TCC (the maximum supply temperature determined according
to section 3.1.9), determine Qh(Tj) and
[Edot]h(Tj) as specified in section 4.2.2
(i.e. Qh(Tj) = Qhp(Tj)
and [Edot]h(Tj) =
[Edot]hp(Tj)). Note: Even though
To(Tj) >= TCC, resistive heating
may be required; evaluate Equation 4.2.1-2 for all bins.
Case 2. For outdoor bin temperatures where
To(Tj) < TCC, determine
Qh(Tj) and [Edot]h(Tj)
using,
Qh(Tj) = Qhp(Tj) +
QCC(Tj) [Edot]h(Tj) =
[Edot]hp(Tj) +
[Edot]CC(Tj)
Where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.115
Note: Even though To(Tj) <
Tcc, additional resistive heating may be required;
evaluate Equation 4.2.1-2 for all bins.
4.2.5.3 Heat pumps having a heat comfort controller: additional
steps for calculating the HSPF of a heat pump having a two-capacity
compressor. Calculate the space heating capacity and electrical
power of the heat pump without the heat comfort controller being
active as specified in section 4.2.3 for both high and low capacity
and at each outdoor bin temperature, Tj, that is listed
in Table 19. Denote these capacities and electrical powers by using
the subscript ``hp'' instead of ``h.'' For the low capacity case,
calculate the mass flow rate (expressed in pounds-mass of dry air
per hour) and the specific heat of the indoor air (expressed in Btu/
lbmda [middot] [deg]F) from the results of the
H11 Test using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.116
Cp,da = 0.24 + 0.444 * Wn
Where
Vis,Vimx, v'n (or vn),
and Wn are defined following Equation 3-1. For each
outdoor bin temperature listed in Table 19, calculate the nominal
temperature of the air leaving the heat pump condenser coil when
operating at low capacity using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.117
Repeat the above calculations to determine the mass flow rate
(mdak=2) and the specific heat of the indoor
air (Cp,dak=2) when operating at high capacity
by using the results of the H12 Test. For each outdoor
bin temperature listed in Table 19, calculate the nominal
temperature of the air leaving the heat pump condenser coil when
operating at high capacity using,
[[Page 69391]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.118
Evaluate eh(Tj)/N, RH(Tj)/N,
Xk=1(Tj), and/or
Xk=2(Tj), PLFj, and
[delta]'(Tj) or [delta]''(Tj) as specified in
section 4.2.3.1. 4.2.3.2, 4.2.3.3, or 4.2.3.4, whichever applies,
for each temperature bin. To evaluate these quantities, use the low-
capacity space heating capacity and the low-capacity electrical
power from Case 1 or Case 2, whichever applies; use the high-
capacity space heating capacity and the high-capacity electrical
power from Case 3 or Case 4, whichever applies.
Case 1. For outdoor bin temperatures where
Tok=1(Tj) is equal to or greater
than TCC (the maximum supply temperature determined
according to section 3.1.9), determine
Qhk=1(Tj) and
[Edot]hk=1(Tj) as specified in
section 4.2.3 (i.e., Qhk=1(Tj) =
Qhpk=1(Tj) and
[Edot]hk=1(Tj) =
[Edot]hpk=1(Tj).
Note: Even though Tok=1(Tj) >=
TCC, resistive heating may be required; evaluate
RH(Tj)/N for all bins.
Case 2. For outdoor bin temperatures where
Tok=1(Tj) < TCC,
determine Qhk=1(Tj) and
[Edot]hk=1(Tj) using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.119
Note: Even though Tok=1(Tj)
>=Tcc, additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
Case 3. For outdoor bin temperatures where
Tok=2(Tj) is equal to or greater
than TCC, determine
Qhk=2(Tj) and
[Edot]hk=2(Tj) as specified in
section 4.2.3 (i.e., Qhk=2(Tj) =
Qhpk=2(Tj) and
[Edot]hk=2(Tj) =
[Edot]hpk=2(Tj)).
Note: Even though Tok=2(Tj) <
TCC, resistive heating may be required; evaluate
RH(Tj)/N for all bins.
Case 4. For outdoor bin temperatures where
Tok=2(Tj) < TCC,
determine Qhk=2(Tj) and
[Edot]hk=2(Tj) using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.120
Note: Even though Tok=2(Tj) <
Tcc, additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
4.2.5.4 Heat pumps having a heat comfort controller: additional
steps for calculating the HSPF of a heat pump having a variable-
speed compressor. [Reserved]
4.2.6 Additional steps for calculating the HSPF of a heat pump
having a triple-capacity compressor. The only triple-capacity heat
pumps covered are triple-capacity, northern heat pumps.
For such heat pumps, the calculation of the Eq. 4.2-1 quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.121
differ depending on whether the heat pump would cycle on and off at
low capacity (section 4.2.6.1), cycle on and off at high capacity
(section 4.2.6.2), cycle on and off at booster capacity (4.2.6.3),
cycle between low and high capacity (section 4.2.6.4), cycle between
high and booster capacity (section 4.2.6.5), operate continuously at
low capacity (4.2.6.6), operate continuously at high capacity
(section 4.2.6.7), operate continuously at booster capacity
(4.2.6.8), or heat solely using resistive heating (also section
4.2.6.8) in responding to the building load. As applicable, the
manufacturer must supply information regarding the outdoor
temperature range at which each stage of compressor capacity is
active. As an informative example, data may be submitted in this
manner: At the low (k=1) compressor capacity, the outdoor
temperature range of operation is 40[emsp14][deg]F <= T <=
65[emsp14][deg]F; At the high (k=2) compressor capacity, the outdoor
temperature range of operation is 20[emsp14][deg]F <= T <=
50[emsp14][deg]F; At the booster (k=3) compressor capacity, the
outdoor temperature range of operation is -20[emsp14][deg]F <= T <=
30[emsp14][deg]F.
a. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at low compressor
capacity and outdoor temperature Tj using the equations given in
section 4.2.3 for Qhk=1(Tj) and
[Edot]hk=1 (Tj)) In evaluating the
section 4.2.3 equations, Determine Qhk=1(62)
and [Edot]hk=1(62) from the H01
Test, Qhk=1(47) and
[Edot]hk=1(47) from the H11 Test,
and Qhk=2(47) and
[Edot]hk=2(47) from the H12 Test.
Calculate all four quantities as specified in section 3.7. If, in
accordance with section 3.6.6, the H31 Test is conducted,
calculate Qhk=1(17) and
[Edot]hk=1(17) as specified in section 3.10
and determine Qhk=1(35) and
[Edot]hk=1(35) as specified in section 3.6.6.
b. Evaluate the space heating capacity and electrical power
consumption (Qhk=2(Tj) and
[Edot]hk=2 (Tj)) of the heat pump
when operating at high compressor capacity and outdoor temperature
Tj by solving Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2.
Determine Qhk=1(62) and
[Edot]hk=1(62) from the H01 Test,
Qhk=1(47) and
[Edot]hk=1(47) from the H11 Test,
and Qhk=2(47) and
[Edot]hk=2(47) from the H12 Test,
evaluated as specified in section 3.7. Determine the equation input
for Qhk=2(35) and
[Edot]hk=2(35) from the H22,
evaluated as
[[Page 69392]]
specified in section 3.9.1. Also, determine
Qhk=2(17) and
[Edot]hk=2(17) from the H32 Test,
evaluated as specified in section 3.10.
c. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at booster compressor
capacity and outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TP09NO15.122
Determine Qhk=3(17) and
[Edot]hk=3(17) from the H33 Test
and determine Qhk=2(2) and
[Edot]hk=3(2) from the H43 Test.
Calculate all four quantities as specified in section 3.10.
Determine the equation input for Qhk=3(35) and
[Edot]hk=3(35) as specified in section 3.6.6.
4.2.6.1 Steady-state space heating capacity when operating at
low compressor capacity is greater than or equal to the building
heating load at temperature Tj,
Qhk=1(Tj) >=BL(Tj)., and
the heat pump permits low compressor capacity at Tj.
Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.123
using Eqs. 4.2.3-1 and 4.2.3-2, respectively. Determine the equation
inputs Xk=1(Tj), PLFj, and
[delta]'(Tj) as specified in section 4.2.3.1. In
calculating the part load factor, PLFj, use the low-
capacity cyclic-degradation coefficient CDh,
[or equivalently, CDh(k=1)] determined in
accordance with section 3.6.6.
4.2.6.2 Heat pump only operates at high (k=2) compressor
capacity at temperature Tj and its capacity is greater
than or equal to the building heating load, BL(Tj) <
Qhk=2(Tj). Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.124
as specified in section 4.2.3.3. Determine the equation inputs
Xk=2(Tj), PLFj, and
[delta]'(Tj) as specified in section 4.2.3.3. In
calculating the part load factor, PLFj, use the high-
capacity cyclic-degradation coefficient,
CDh(k=2) determined in accordance with section
3.6.6.
4.2.6.3 Heat pump only operates at high (k=3) compressor
capacity at temperature Tj and its capacity is greater
than or equal to the building heating load, BL(Tj) <=
Qhk=3(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.125
Determine the low temperature cut-out factor,
[delta]'(Tj), using Eq. 4.2.3-3. Use the booster-capacity
cyclic-degradation coefficient, CDh(k=3)
determined in accordance with section 3.6.6.
4.2.6.4 Heat pump alternates between high (k=2) and low (k=1)
compressor capacity to satisfy the building heating load at a
temperature Tj,
Qhk=1(Tj) < BL(Tj) <
Qhk=2(Tj). Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.126
[[Page 69393]]
as specified in section 4.2.3.2. Determine the equation inputs
Xk=1(Tj), Xk=2(Tj), and
[delta]'(Tj) as specified in section 4.2.3.2.
4.2.6.5 Heat pump alternates between high (k=2) and booster
(k=3) compressor capacity to satisfy the building heating load at a
temperature Tj,
Qhk=2(Tj) j)
hk=3(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.127
and Xk=3(Tj) = Xk=2(Tj)
= the heating mode, booster capacity load factor for temperature bin
j, dimensionless. Determine the low temperature cut-out factor,
[delta]'(Tj), using Eq. 4.2.3-3.
4.2.6.6 Heat pump only operates at low (k=1) capacity at
temperature Tj and its capacity is less than the building
heating load, BL(Tj) >
Qhk=1(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.128
Where the low temperature cut-out factor, [delta]'(Tj), is
calculated using Eq. 4.2.3-3.
4.2.6.7 Heat pump only operates at high (k = 2) capacity at
temperature Tj and its capacity is less than the building heating
load, BL(Tj) > Qhk=2(Tj).Evaluate
the quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.129
as specified in section 4.2.3.4. Calculate [delta]''(Tj) using
the equation given in section 4.2.3.4.
4.2.6.8 Heat pump only operates at booster (k = 3) capacity at
temperature Tj and its capacity is less than the building heating
load, BL(Tj) >
Qhk=3(Tj). or the system converts
to using only resistive heating.
[GRAPHIC] [TIFF OMITTED] TP09NO15.130
Where [delta]''(Tj) is calculated as specified in section 4.2.3.4 if
the heat pump is operating at its booster compressor capacity. If
the heat pump system converts to using only resistive heating at
outdoor temperature Tj, set [delta]'(Tj) equal
to zero.
4.2.7 Additional steps for calculating the HSPF of a heat pump
having a single indoor unit with multiple blowers. The calculation
of the Eq. 4.2-1 quantities eh(Tj)/N and
RH(Tj)/N are evaluated as specified in applicable below
subsection.
4.2.7.1 For multiple blower heat pumps that are connected to a
singular, single-speed outdoor unit.
a. Calculate the space heating capacity, Qhk= 1(Tj),
and electrical power consumption, [Edot]hk= 1 (Tj), of
the heat pump when operating at the heating minimum air volume rate
and outdoor temperature Tj using Eqs. 4.2.2-3 and 4.2.2-
4, respectively. Use these same equations to calculate the space
heating capacity, Qhk= 2 (Tj) and electrical power
consumption, [Edot]hk= 2 (Tj), of the test unit when
operating at the heating full-load air volume rate and outdoor
temperature Tj. In evaluating Eqs. 4.2.2-3 and 4.2.2- 4,
determine the quantities Qhk= 1 (47) and
[Edot]hk= 1 (47) from the H11 Test; determine
Qhk= 2 (47) and [Edot]hk= 2 (47) from the
H12 Test. Evaluate all four quantities according to
section 3.7. Determine the quantities Qhk= 1 (35) and
[Edot]hk= 1 (35) as specified in section 3.6.2. Determine
Qhk= 2 (35) and [Edot]hk= 2 (35) from the
H22 Frost Accumulation Test as calculated according to
section 3.9.1. Determine the quantities Qhk= 1 (17) and
[Edot]hk= 1 (17) from the H31 Test, and
Qhk= 2 (17) and [Edot]hk= 2 (17) from the
H32 Test. Evaluate all four quantities according to
section 3.10. Refer to section 3.6.2 and Table 11 for additional
information on the referenced laboratory tests.
b. Determine the heating mode cyclic degradation coefficient,
CDh, as per sections 3.6.2 and 3.8 to 3.8.1. Assign this
same value to CDh(k = 2).
c. Except for using the above values of Qhk= 1 (Tj),
[Edot]hk= 1 (Tj), Qhk= 2 (Tj),
[Edot]hk= 2 (Tj), CDh, and CDh(k =
2), calculate the quantities eh(Tj)/N as
specified in section 4.2.3.1 for cases where Qhk= 1 (Tj)
>= BL(Tj). For all other outdoor bin temperatures,
Tj, calculate eh(Tj)/N and RHh(Tj)/
N as specified in section 4.2.3.3 if Qhk= 2 (Tj) > BL(Tj)
or as specified in section 4.2.3.4 if Qhk= 2 (Tj) <=
BL(Tj)
4.2.7.2 For multiple blower heat pumps connected to either a
lone outdoor unit with a two-capacity compressor or to two separate
but identical model single-speed outdoor units. Calculate the
quantities eh(Tj)/N and RH(Tj)/N as
specified in section 4.2.3.
4.3 Calculations of Off-mode Seasonal Power and Energy
Consumption.
4.3.1 For central air conditioners and heat pumps with a cooling
capacity of:
[[Page 69394]]
less than 36,000 Btu/h, determine the off mode rating, PW,OFF,
with the following equation:
[GRAPHIC] [TIFF OMITTED] TP09NO15.131
greater than or equal to 36,000 Btu/h, calculate the capacity
scaling factor according to:
[GRAPHIC] [TIFF OMITTED] TP09NO15.132
Where, QC(95) is the total cooling capacity at the A or
A2 Test condition, and determine
[GRAPHIC] [TIFF OMITTED] TP09NO15.133
4.3.2 Calculate the off mode energy consumption for both central
air conditioner and heat pumps for the shoulder season, E1, using:
E1 = P1 [middot] SSH; and the off mode energy consumption of a CAC,
only, for the heating season, E2, using: E2 = P2 [middot] HSH; where
P1 and P2 is determined in Section 3.13. HSH can be determined by
multiplying the heating season-hours from Table 21 with the
fractional Bin-hours, from Table 19, that pertain to the range of
temperatures at which the crankcase heater operates. If the
crankcase heater is controlled to disable for the heating season,
the temperature range at which the crankcase heater operates is
defined to be from 72 [deg]F to five degrees Fahrenheit below a
turn-off temperature specified by the manufacturer in the DOE
Compliance Certification Database. If the crankcase heater is
operated during the heating season, the temperature range at which
the crankcase heater operates is defined to be from 72 [deg]F to -23
[deg]F, the latter of which is a temperature that sets the range of
Bin-hours to encompass all outside air temperatures in the heating
season.
SSH can be determined by multiplying the shoulder season-hours
from Table 21 with the fractional Bin-hours in Table 22.
Table 21--Representative Cooling and Heating Load Hours and the Corresponding Set of Seasonal Hours for Each
Generalized Climatic Region
----------------------------------------------------------------------------------------------------------------
Shoulder
Climatic region Cooling load Heating load Cooling season Heating season season hours
hours CLHR hours HLHR hours CSHR hours HSHR SSHR
----------------------------------------------------------------------------------------------------------------
I............................... 2400 750 6731 1826 203
II.............................. 1800 1250 5048 3148 564
III............................. 1200 1750 3365 4453 942
IV.............................. 800 2250 2244 5643 873
Rating Values................... 1000 2080 2805 5216 739
V............................... 400 2750 1122 6956 682
VI.............................. 200 2750 561 6258 1941
----------------------------------------------------------------------------------------------------------------
[GRAPHIC] [TIFF OMITTED] TP09NO15.134
Region I: HSH = 2.4348HLH;
Region II: HSH = 2.5182HLH;
Region III: HSH = 2.5444HLH;
[[Page 69395]]
Region IV: HSH = 2.5078HLH;
Region V: HSH = 2.5295HLH;
Region VI: HSH = 2.2757HLH.
SSH is evaluated: SSH = 8760 - (CSH + HSH), where CSH = the
cooling season hours calculated using CSH = 2.8045 [middot] CLH
Table 22--Fractional Bin Hours for the Shoulder Season Hours for All
Regions
------------------------------------------------------------------------
Fractional bin hours
---------------------------------
Tj([deg]F) Air
conditioners Heat pumps
------------------------------------------------------------------------
72.................................... 0.333 0.167
67.................................... 0.667 0.333
62.................................... 0 0.333
57.................................... 0 0.167
------------------------------------------------------------------------
[GRAPHIC] [TIFF OMITTED] TP09NO15.135
4.3.4 For air conditioners, the annual off mode energy
consumption, ETOTAL, is: ETOTAL = E1 + E2.
4.3.5 For heat pumps, the annual off mode energy consumption,
ETOTAL, is E1.
4.4 Calculations of the Actual and Representative Regional
Annual Performance Factors for Heat Pumps.
4.4.1 Calculation of actual regional annual performance factors
(APFA) for a particular location and for each
standardized design heating requirement.
[GRAPHIC] [TIFF OMITTED] TP09NO15.136
Where,
CLHA = the actual cooling hours for a particular location
as determined using the map given in Figure 2, hr.
Qc\k\(95) = the space cooling capacity of the unit as
determined from the A or A2 Test, whichever applies, Btu/
h.
HLHA = the actual heating hours for a particular location
as determined using the map given in Figure 1, hr.
DHR = the design heating requirement used in determining the HSPF;
refer to section 4.2 and see section 1.2, Definitions, Btu/h.
C = defined in section 4.2 following Equation 4.2-2, dimensionless.
SEER = the seasonal energy efficiency ratio calculated as specified
in section 4.1, Btu/W[middot]h.
HSPF = the heating seasonal performance factor calculated as
specified in section 4.2 for the generalized climatic region that
includes the particular location of interest (see Figure 1), Btu/
W[middot]h. The HSPF should correspond to the actual design heating
requirement (DHR), if known. If it does not, it may correspond to
one of the standardized design heating requirements referenced in
section 4.2.
P1 is the shoulder season per-compressor off mode power, as
determined in section 3.13, W.
SSH is the shoulder season hours, hr.
P2 is the heating season per-compressor off mode power, as
determined in section 3.13, W.
HSH is the heating season hours, hr.
4.4.2 Calculation of representative regional annual performance
factors (APFR) for each generalized climatic region and
for each standardized design heating requirement.
[GRAPHIC] [TIFF OMITTED] TP09NO15.137
Where,
CLHR = the representative cooling hours for each
generalized climatic region, Table 23, hr.
HLHR = the representative heating hours for each
generalized climatic region, Table 23, hr.
HSPF = the heating seasonal performance factor calculated as
specified in section 4.2 for the each generalized climatic region
and for each standardized design heating requirement within each
region, Btu/W.h.
The SEER, Qc\k\(95), DHR, and C are the same
quantities as defined in section 4.3.1. Figure 1 shows the
generalized climatic regions. Table 20 lists standardized design
heating requirements.
Table 23--Representative Cooling and Heating Load Hours for Each
Generalized Climatic Region
------------------------------------------------------------------------
Region CLHR HLHR
------------------------------------------------------------------------
I....................................... 2400 750
II...................................... 1800 1250
III..................................... 1200 1750
[[Page 69396]]
IV...................................... 800 2250
V....................................... 400 2750
VI...................................... 200 2750
------------------------------------------------------------------------
4.5. Rounding of SEER, HSPF, and APF for reporting purposes.
After calculating SEER according to section 4.1, HSPF according to
section 4.2, and APF according to section 4.3, round the values off
as specified in subpart B 430.23(m) of Title 10 of the Code of
Federal Regulations.
[GRAPHIC] [TIFF OMITTED] TP09NO15.138
[GRAPHIC] [TIFF OMITTED] TP09NO15.139
[[Page 69397]]
4.6 Calculations of the SHR, which should be computed for
different equipment configurations and test conditions specified in
Table 24.
Table 24--Applicable Test Conditions for Calculation of the Sensible Heat Ratio
----------------------------------------------------------------------------------------------------------------
Reference
Equipment configuration Table No. of SHR computation with Computed values
Appendix M results from
----------------------------------------------------------------------------------------------------------------
Units Having a Single-Speed Compressor 4 B Test.................... SHR(B).
and a Fixed-Speed Indoor blower, a
Constant Air Volume Rate Indoor blower,
or No Indoor blower.
Units Having a Single-Speed Compressor 5 B2 and B1 Tests........... SHR(B1), SHR(B2).
That Meet the Section 3.2.2.1 Indoor
Unit Requirements.
Units Having a Two-Capacity Compressor.. 6 B2 and B1 Tests........... SHR(B1), SHR(B2).
Units Having a Variable-Speed Compressor 7 B2 and B1 Tests........... SHR(B1), SHR(B2).
----------------------------------------------------------------------------------------------------------------
The SHR is defined and calculated as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.140
Where both the total and sensible cooling capacities are
determined from the same cooling mode test and calculated from data
collected over the same 30-minute data collection interval.
4.7 calculations of the Energy Efficiency Ratio (EER). Calculate
the energy efficiency ratio using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.141
Where Qc\k\(T) and [Edot]c\k\(T) are the
space cooling capacity and electrical power consumption determined
from the 30-minute data collection interval of the same steady-state
wet coil cooling mode test and calculated as specified in section
3.3. Add the letter identification for each steady-state test as a
subscript (e.g., EERA2) to differentiate among the
resulting EER values.
0
11. Add appendix M1 to subpart B of part 430 to read as follows:
APPENDIX M1 TO SUBPART B OF PART 430--UNIFORM TEST METHOD FOR MEASURING
THE ENERGY CONSUMPTION OF CENTRAL AIR CONDITIONERS AND HEAT PUMPS
Note: Prior to May 9, 2016, any representations, including
compliance certifications, made with respect to the energy use,
power, or efficiency of central air conditioners and central air
conditioning heat pumps must be based on the results of testing
pursuant to either Appendix M or the procedures in Appendix M as it
appeared at 10 CFR part 430, subpart B, Appendix M, in the 10 CFR
parts 200 to 499 edition revised as of January 1, 2015. Any
representations made with respect to the energy use or efficiency of
such central air conditioners and central air conditioning heat
pumps must be in accordance with whichever version is selected.
On or after May 9, 2016 and prior to the compliance date for any
amended energy conservation standards, any representations,
including compliance certifications, made with respect to the energy
use, power, or efficiency of central air conditioners and central
air conditioning heat pumps must be based on the results of testing
pursuant to Appendix M.
On or after the compliance date for any amended energy
conservation standards, any representations, including compliance
certifications, made with respect to the energy use, power, or
efficiency of central air conditioners and central air conditioning
heat pumps must be based on the results of testing pursuant to this
appendix (Appendix M1).
1. Scope and Definitions
1.1 Scope.
This test procedure provides a method of determining SEER, EER,
HSPF and PW,OFF for central air conditioners and central
air conditioning heat pumps including the following categories:
(a) Split-system air conditioners; and single-zone-multiple-coil,
multi-split (including VRF), and multi-circuit systems
(b) Split-system heat pumps and single-zone-multiple-coil, multi-
split (including VRF), and multi-circuit systems
(c) Single-package air conditioners
(d) Single-package heat pumps
(e) Small-duct, high-velocity systems (including VRF)
(f) Space-constrained products--air conditioners
(g) Space-constrained products--heat pumps
For purposes of this appendix, the Department of Energy
incorporates by reference specific sections of several industry
standards, as listed in Sec. 430.3. In cases where there is a
conflict, the language of the test procedure in this appendix takes
precedence over the incorporated standards.
All section references refer to sections within this appendix
unless otherwise stated.
[[Page 69398]]
1.2. Definitions
Airflow-control settings are programmed or wired control system
configurations that control a fan to achieve discrete, differing
ranges of airflow--often designated for performing a specific
function (e.g., cooling, heating, or constant circulation)--without
manual adjustment other than interaction with a user-operable
control (i.e., a thermostat) that meets the manufacturer
specifications for installed-use. For the purposes of this appendix,
manufacturer specifications for installed-use are those found in the
product literature shipped with the unit.
Airflow prevention device denotes a device(s) that prevents
airflow via natural convection by mechanical means, such as an air
damper box, or by means of changes in duct height, such as an
upturned duct.
Annual performance factor means the total heating and cooling
done by a heat pump in a particular region in one year divided by
the total electric energy used in one year.
Blower coil indoor unit means the indoor unit of a split-system
central air conditioner or heat pump that includes a refrigerant-to-
air heat exchanger coil, may include a cooling-mode expansion
device, and includes either an indoor blower housed with the coil or
a separate designated air mover such as a furnace or a modular
blower (as defined in Appendix AA). Blower coil system refers to a
split-system that includes one or more blower coil indoor units.
CFR means Code of Federal Regulations.
Coefficient of Performance (COP) means the ratio of the average
rate of space heating delivered to the average rate of electrical
energy consumed by the heat pump. These rate quantities must be
determined from a single test or, if derived via interpolation, must
be determined at a single set of operating conditions. COP is a
dimensionless quantity. When determined for a ducted unit tested
without an indoor blower installed, COP must include the section
3.7and 3.9.1 default values for the heat output and power input of a
fan motor.
Coil-only indoor unit means the indoor unit of a split-system
central air conditioner or heat pump that includes a refrigerant-to-
air heat exchanger coil and may include a cooling-mode expansion
device, but does not include an indoor blower housed with the coil,
and does not include a separate designated air mover such as a
furnace or a modular blower (as defined in Appendix AA). A coil-only
indoor unit is designed to use a separately-installed furnace or a
modular blower for indoor air movement.
Coil-only system refers to a system that includes one or more
coil-only indoor units.
Condensing unit removes the heat absorbed by the refrigerant to
transfer it to the outside environment, and which consists of an
outdoor coil, compressor(s), and air moving device.
Constant-air-volume-rate indoor blower means a fan that varies
its operating speed to provide a fixed air-volume-rate from a ducted
system.
Continuously recorded, when referring to a dry bulb measurement,
dry bulb temperature used for test room control, wet bulb
temperature, dew point temperature, or relative humidity
measurements, means that the specified value must be sampled at
regular intervals that are equal to or less than 5 seconds.
Cooling load factor (CLF) means the ratio having as its
numerator the total cooling delivered during a cyclic operating
interval consisting of one ON period and one OFF period. The
denominator is the total cooling that would be delivered, given the
same ambient conditions, had the unit operated continuously at its
steady-state, space-cooling capacity for the same total time (ON +
OFF) interval.
Crankcase heater means any electrically powered device or
mechanism for intentionally generating heat within and/or around the
compressor sump volume often done to minimize the dilution of the
compressor's refrigerant oil by condensed refrigerant. Crankcase
heater control may be achieved using a timer or may be based on a
change in temperature or some other measurable parameter, such that
the crankcase heater is not required to operate continuously. A
crankcase heater without controls operates continuously when the
compressor is not operating.
Cyclic Test means a test where the unit's compressor is cycled
on and off for specific time intervals. A cyclic test provides half
the information needed to calculate a degradation coefficient.
Damper box means a short section of duct having an air damper
that meets the performance requirements of section 2.5.7.
Degradation coefficient (CD) means a parameter used
in calculating the part load factor. The degradation coefficient for
cooling is denoted by CD\c\. The degradation coefficient
for heating is denoted by CD\h\.
Demand-defrost control system means a system that defrosts the
heat pump outdoor coil only when measuring a predetermined
degradation of performance. The heat pump's controls monitor one or
more parameters that always vary with the amount of frost
accumulated on the outdoor coil (e.g., coil to air differential
temperature, coil differential air pressure, outdoor fan power or
current, optical sensors) at least once for every ten minutes of
compressor ON-time when space heating. One acceptable alternative to
the criterion given in the prior sentence is a feedback system that
measures the length of the defrost period and adjusts defrost
frequency accordingly. In all cases, when the frost parameter(s)
reaches a predetermined value, the system initiates a defrost. In a
demand-defrost control system, defrosts are terminated based on
monitoring a parameter(s) that indicates that frost has been
eliminated from the coil. (Note: Systems that vary defrost intervals
according to outdoor dry-bulb temperature are not demand-defrost
systems.) A demand-defrost control system, which otherwise meets the
above requirements, may allow time-initiated defrosts if, and only
if, such defrosts occur after 6 hours of compressor operating time.
Design heating requirement (DHR) predicts the space heating load
of a residence when subjected to outdoor design conditions.
Estimates for the DHR are provided for six generalized U.S. climatic
regions in section 4.2.
Dry-coil tests are cooling mode tests where the wet-bulb
temperature of the air supplied to the indoor coil is maintained low
enough that no condensate forms on this coil.
Ducted system means an air conditioner or heat pump that is
designed to be permanently installed equipment and delivers
conditioned air to the indoor space through a duct(s). The air
conditioner or heat pump may be either a split-system or a single-
package unit.
Energy efficiency ratio (EER) means the ratio of the average
rate of space cooling delivered to the average rate of electrical
energy consumed by the air conditioner or heat pump. These rate
quantities must be determined from a single test or, if derived via
interpolation, must be determined at a single set of operating
conditions. EER is expressed in units of
[GRAPHIC] [TIFF OMITTED] TP09NO15.142
When determined for a ducted unit tested without an indoor blower
installed, EER must include the section 3.3 and 3.5.1 default values
for the heat output and power input of a fan motor.
Evaporator coil absorbs heat from an enclosed space and
transfers the heat to a refrigerant.
Heat pump means a kind of central air conditioner, which
consists of one or more assemblies, utilizing an indoor conditioning
coil, compressor, and refrigerant-to-outdoor air heat exchanger to
provide air heating, and may also provide air cooling, air
dehumidifying, air humidifying, air circulating, and air cleaning.
Heat pump having a heat comfort controller means equipment that
regulates the operation of the electric resistance elements to
assure that the air temperature leaving the indoor section does not
fall below a specified temperature. This specified temperature is
usually field adjustable. Heat pumps that actively regulate the rate
of electric resistance heating when operating below the balance
point (as the result of a second stage call from the thermostat) but
do not operate to maintain a minimum delivery temperature are not
considered as having a heat comfort controller.
Heating load factor (HLF) means the ratio having as its
numerator the total heating delivered during a cyclic operating
interval consisting of one ON period and one OFF period. The
denominator is the total heating that would be delivered, given the
same ambient conditions, if the unit operated continuously at its
steady-state space heating capacity for the same total time (ON plus
OFF) interval.
Heating season means the months of the year that require
heating, e.g., typically, and roughly, October through April.
Heating seasonal performance factor (HSPF) means the total space
heating required during the space heating season, expressed in
Btu's, divided by the total electrical energy consumed by the heat
pump system during the same season, expressed in watt-hours. The
HSPF used to evaluate compliance with the Energy Conservation
Standards (see 10 CFR 430.32(c)) is based on Region IV, the design
heating requirement,
[[Page 69399]]
and the sampling plan stated in 10 CFR 429.16(a).
Independent coil manufacturer (ICM) means a manufacturer that
manufactures indoor units but does not manufacture single-package
units or outdoor units.
Indoor unit transfers heat between the refrigerant and the
indoor air and consists of an indoor coil and casing and may include
a cooling mode expansion device and/or an air moving device.
Multiple-circuit (or multi-circuit) system means a split system
that has one outdoor unit and that has two or more indoor units
installed on two or more refrigeration circuits such that each
refrigeration circuit serves a compressor and one and only one
indoor unit, and refrigerant is not shared from circuit to circuit.
Multiple-split (or multi-split) system means a split system that
has one outdoor unit and two or more indoor coil-only or indoor
blower coil units connected to its other component(s) with a single
refrigerant circuit. The indoor units operate independently and can
condition multiple zones in response to at least two indoor
thermostats or temperature sensors. The outdoor unit operates in
response to independent operation of the indoor units based on
control input of multiple indoor thermostats or temperature sensors,
and/or based on refrigeration circuit sensor input (e.g., suction
pressure).
Nominal capacity means the capacity that is claimed by the
manufacturer in the product name plate. Nominal cooling capacity is
approximate to the air conditioner cooling capacity tested at A or
A2 condition. Nominal heating capacity is approximate to the heat
pump heating capacity tested in H12 test (or the optional H1N test).
Non-ducted system means a split-system central air conditioner
or heat pump that is designed to be permanently installed and that
directly heats or cools air within the conditioned space using one
or more indoor units that are mounted on room walls and/or ceilings.
The system may be of a modular design that allows for combining
multiple outdoor coils and compressors to create one overall system.
Normalized Gross Indoor Fin Surface (NGIFS) means the gross fin
surface area of the indoor unit coil divided by the cooling capacity
measured for the A or A2 Test whichever applies.
Off-mode power consumption means the power consumption when the
unit is connected to its main power source but is neither providing
cooling nor heating to the building it serves.
Off-mode season means, for central air conditioners, the
shoulder season and the entire heating season; and for heat pumps,
the shoulder season only.
Outdoor unit transfers heat between the refrigerant and the
outdoor air, and consists of an outdoor coil, compressor(s), an air
moving device, and in addition for heat pumps, could include a
heating mode expansion device, reversing valve, and defrost
controls.
Outdoor unit manufacturer (OUM) means a manufacturer of single-
package units, outdoor units, and/or both indoor units and outdoor
units.
Part-load factor (PLF) means the ratio of the cyclic energy
efficiency ratio (coefficient of performance) to the steady-state
energy efficiency ratio (coefficient of performance), where both
energy efficiency ratios (coefficients of performance) are
determined based on operation at the same ambient conditions.
Seasonal energy efficiency ratio (SEER) means the total heat
removed from the conditioned space during the annual cooling season,
expressed in Btu's, divided by the total electrical energy consumed
by the central air conditioner or heat pump during the same season,
expressed in watt-hours.
Short ducted system means a ducted split system whose one or
more indoor sections produce greater than zero but no greater than
0.1 inches (of water) of external static pressure when operated at
the full-load air volume not exceeding 450 cfm per rated ton of
cooling.
Shoulder season means the months of the year in between those
months that require cooling and those months that require heating,
e.g., typically, and roughly, April through May, and September
through October.
Single-package unit means any central air conditioner or heat
pump that has all major assemblies enclosed in one cabinet.
Single-split-system means a split system that has one outdoor
unit and that has one indoor coil-only or indoor blower coil unit
connected to its other component(s) with a single refrigeration
circuit.
Single-zone-multiple-coil split system means a split system that
has one outdoor unit and that has two or more indoor units connected
with a single refrigeration circuit. The indoor units operate in
unison in response to a single indoor thermostat.
Small-duct, high-velocity system means a system that contains a
blower and indoor coil combination that is designed for, and
produces, at least 1.2 inches (of water) of external static pressure
when operated at the full-load air volume rate of 220-350 cfm per
rated ton of cooling. When applied in the field, uses high-velocity
room outlets (i.e., generally greater than 1000 fpm) having less
than 6.0 square inches of free area.
Split system means any air conditioner or heat pump that has one
or more of the major assemblies separated from the others. Split-
systems may be either blower coil systems or coil-only systems.
Standard Air means dry air having a mass density of 0.075 lb/ft
\3\.
Steady-state test means a test where the test conditions are
regulated to remain as constant as possible while the unit operates
continuously in the same mode.
Temperature bin means the 5[emsp14][deg]F increments that are
used to partition the outdoor dry-bulb temperature ranges of the
cooling (>=65[emsp14][deg]F) and heating (<65[emsp14][deg]F)
seasons.
Test condition tolerance means the maximum permissible
difference between the average value of the measured test parameter
and the specified test condition.
Test operating tolerance means the maximum permissible range
that a measurement may vary over the specified test interval. The
difference between the maximum and minimum sampled values must be
less than or equal to the specified test operating tolerance.
Tested combination means a single-zone-multiple-coil, multi-
split, or multi-circuit system having the following features:
(1) The system consists of one outdoor unit with one or more
compressors matched with between two and five indoor units;
(2) The indoor units shall:
(i) Collectively, have a nominal cooling capacity greater than
or equal to 95 percent and less than or equal to 105 percent of the
nominal cooling capacity of the outdoor unit;
(ii) Represent the highest sales volume model family that can
meet the 95 percent nominal cooling capacity of the outdoor unit
[Note: another indoor model family may be used if five indoor units
from the highest sales volume model family do not provide sufficient
capacity to meet the 95 percent threshold level].
(iii) Individually not have a nominal cooling capacity greater
than 50 percent of the nominal cooling capacity of the outdoor unit,
unless the nominal cooling capacity of the outdoor unit is 24,000
Btu/h or less;
(iv) Operate at fan speeds consistent with manufacturer's
specifications; and
(v) All be subject to the same minimum external static pressure
requirement while able to produce the same external static pressure
at the exit of each outlet plenum when connected in a manifold
configuration as required by the test procedure.
(vi) Where referenced, ``nominal cooling capacity'' is to be
interpreted for indoor units as the highest cooling capacity listed
in published product literature for 95 [deg]F outdoor dry bulb
temperature and 80 [deg]F dry bulb, 67 [deg]F wet bulb indoor
conditions, and for outdoor units as the lowest cooling capacity
listed in published product literature for these conditions. If
incomplete or no operating conditions are reported, the highest (for
indoor units) or lowest (for outdoor units) such cooing capacity
shall be used.
Time-adaptive defrost control system is a demand-defrost control
system that measures the length of the prior defrost period(s) and
uses that information to automatically determine when to initiate
the next defrost cycle.
Time-temperature defrost control systems initiate or evaluate
initiating a defrost cycle only when a predetermined cumulative
compressor ON-time is obtained. This predetermined ON-time is
generally a fixed value (e.g., 30, 45, 90 minutes) although it may
vary based on the measured outdoor dry-bulb temperature. The ON-time
counter accumulates if controller measurements (e.g., outdoor
temperature, evaporator temperature) indicate that frost formation
conditions are present, and it is reset/remains at zero at all other
times. In one application of the control scheme, a defrost is
initiated whenever the counter time equals the predetermined ON-
time. The counter is reset when the defrost cycle is completed.
In a second application of the control scheme, one or more
parameters are measured (e.g., air and/or refrigerant temperatures)
at the predetermined, cumulative, compressor ON-time. A defrost is
initiated only if the measured parameter(s) falls within a
predetermined range. The ON-
[[Page 69400]]
time counter is reset regardless of whether or not a defrost is
initiated. If systems of this second type use cumulative ON-time
intervals of 10 minutes or less, then the heat pump may qualify as
having a demand defrost control system (see definition).
Triple-capacity, northern heat pump means a heat pump that
provides two stages of cooling and three stages of heating. The two
common stages for both the cooling and heating modes are the low
capacity stage and the high capacity stage. The additional heating
mode stage is the booster capacity stage, which offers the highest
heating capacity output for a given set of ambient operating
conditions.
Triple-split system means a central air conditioner or heat pump
that is composed of three separate components: An outdoor fan coil
section, an indoor blower coil section, and an indoor compressor
section.
Two-capacity (or two-stage) compressor system means a central
air conditioner or heat pump that has a compressor or a group of
compressors operating with only two stages of capacity.
For such systems, low capacity means the compressor(s) operating
at low stage, or at low load test conditions. The low compressor
stage for heating mode tests may be the same or different from the
cooling mode value.
For such systems, high capacity means the compressor(s)
operating at low stage, or at full load test conditions.
Two-capacity, northern heat pump means a heat pump that has a
factory or field-selectable lock-out feature to prevent space
cooling at high-capacity. Two-capacity heat pumps having this
feature will typically have two sets of ratings, one with the
feature disabled and one with the feature enabled. The certified
indoor coil model number should reflect whether the ratings pertain
to the lockout enabled option via the inclusion of an extra
identifier, such as ``+LO''. When testing as a two-capacity,
northern heat pump, the lockout feature must remain enabled for all
tests.
Variable refrigerant flow (VRF) system means a multi-split
system with at least three compressor capacity stages, distributing
refrigerant through a piping network to multiple indoor blower coil
units each capable of individual zone temperature control, through
proprietary zone temperature control devices and a common
communications network. Single-phase VRF systems less than 65,000
Btu/h are a kind of central air conditioners and central air
conditioning heat pumps.
Variable-speed compressor system means a central air conditioner
or heat pump that has a compressor that uses a variable-speed drive
to vary the compressor speed to achieve variable capacities.
For such a system, maximum speed means the maximum operating
speed, measured by RPM or frequency (Hz), that the unit is designed
to operate in cooling mode or heating mode. Maximum speed does not
change with ambient temperature, and it can be different from
cooling mode to heating mode. Maximum speed does not necessarily
mean maximum capacity.
For such systems, minimum speed means the minimum speed,
measured by RPM or frequency (Hz), that the unit is designed to
operate in cooling mode or heating mode. Minimum speed does not
change with ambient temperature, and it can be different from
cooling mode to heating mode. Minimum speed does not necessarily
mean minimum capacity.
Wet-coil test means a test conducted at test conditions that
typically cause water vapor to condense on the test unit evaporator
coil.
2. Testing Overview and Conditions
(A) Test VRF systems using ANSI/AHRI Standard 1230-2010 sections
3 (except 3.8, 3.9, 3.13, 3.14, 3.15, 3.16, 3.23, 3.24, 3.26, 3.27,
3.28, 3.29, 3.30, and 3.31), 5.1.3, 5.1.4, 6.1.5 (except Table 8),
6.1.6, and 6.2 (incorporated by reference, see Sec. 430.3) and
Appendix M. Where ANSI/AHRI Standard 1230-2010 refers to the
Appendix C therein substitute the provisions of this appendix. In
cases where there is a conflict, the language of the test procedure
in this appendix takes precedence over ANSI/AHRI Standard 1230-2010.
For definitions use section 1 of Appendix M and section 3 of
ANSI/AHRI Standard 1230-2010, excluding sections 3.8, 3.9, 3.13,
3.14, 3.15, 3.16, 3.23, 3.24, 3.26, 3.27, 3.28, 3.29, 3.30, and
3.31. For rounding requirements refer to Sec. 430.23 (m). For
determination of certified rating requirements refer to Sec.
429.16.
For test room requirements, refer to section 2.1 from Appendix
M. For test unit installation requirements refer to sections 2.2.a,
2.2.b, 2.2.c, 2.2.1, 2.2.2, 2.2.3(a), 2.2.3(c), 2.2.4, 2.2.5, and
2.4 to 2.12 from Appendix M, and sections 5.1.3 and 5.1.4 of ANSI/
AHRI Standard 1230-2010.
For general requirements for the test procedure refer to section
3.1 of Appendix M, except for sections 3.1.3 and 3.1.4, which are
requirements for indoor air volume and outdoor air volume. For
indoor air volume and outdoor air volume requirements, refer instead
to section 6.1.5 (except Table 8) and 6.1.6 of ANSI/AHRI Standard
1230-2010. For external static pressure requirements, refer to Table
3 in Appendix M.
For the test procedure, refer to sections 3.3 to 3.5 and 3.7 to
3.13 in Appendix M. For cooling mode and heating mode test
conditions, refer to section 6.2 of ANSI/AHRI Standard 1230-2010.
For calculations of seasonal performance descriptors use section 4
of Appendix M.
(B) For systems other than VRF, only a subset of the sections
listed in this test procedure apply when testing and rating a
particular unit. Table 1 shows the sections of the test procedure
that apply to each system. This table is meant to assist
manufacturers in finding the appropriate sections of the test
procedure; the appendix sections rather than the table provide the
specific requirements for testing, and given the varied nature of
available units, manufacturers are responsible for determining which
sections apply to each unit tested. To use this table, first refer
to the sections listed under ``all units''. Then refer to additional
requirements based on:
(1) System configuration(s),
(2) The compressor staging or modulation capability, and
(3) Any special features.
Testing requirements for space-constrained products do not
differ from similar equipment that is not space-constrained and thus
are not listed separately in this table. Air conditioners and heat
pumps are not listed separately in this table, but heating
procedures and calculations apply only to heat pumps.
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2.1 Test room requirements.
a. Test using two side-by-side rooms, an indoor test room and an
outdoor test room. For multiple-split, single-zone-multi-coil or
multi-circuit air conditioners and heat
[[Page 69404]]
pumps, however, use as many available indoor test rooms as needed to
accommodate the total number of indoor units. These rooms must
comply with the requirements specified in sections 8.1.2 and 8.1.3
of ASHRAE Standard 37-2009 (incorporated by reference, see Sec.
430.3).
b. Inside these test rooms, use artificial loads during cyclic
tests and Frost Accumulation tests, if needed, to produce stabilized
room air temperatures. For one room, select an electric resistance
heater(s) having a heating capacity that is approximately equal to
the heating capacity of the test unit's condenser. For the second
room, select a heater(s) having a capacity that is close to the
sensible cooling capacity of the test unit's evaporator. When
applied, cycle the heater located in the same room as the test unit
evaporator coil ON and OFF when the test unit cycles ON and OFF.
Cycle the heater located in the same room as the test unit
condensing coil ON and OFF when the test unit cycles OFF and ON.
2.2 Test unit installation requirements.
a. Install the unit according to section 8.2 of ASHRAE Standard
37-2009 (incorporated by reference, see Sec. 430.3), subject to the
following additional requirements:
(1) When testing split systems, follow the requirements given in
section 6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see
Sec. 430.3) with Addendum 1 and 2. For the vapor refrigerant
line(s), use the insulation included with the unit; if no insulation
is provided, refer to the specifications for the insulation in the
installation instructions included with the unit by the
manufacturer; if no insulation is included with the unit and the
installation instructions do not contain provisions for insulating
the line(s), fully insulate the vapor refrigerant line(s) with vapor
proof insulation having an inside diameter that matches the
refrigerant tubing and a nominal thickness of at least 0.5 inches.
For the liquid refrigerant line(s), use the insulation included with
the unit; if no insulation is provided, refer to the specifications
for the insulation in the installation instructions included with
the unit by the manufacturer; if no insulation is included with the
unit and the installation instructions do not contain provisions for
insulating the line(s), leave the liquid refrigerant line(s) exposed
to the air for air conditioners and heat pumps that heat and cool;
or, for heating-only heat pumps, insulate the liquid refrigerant
line(s) with insulation having an inside diameter that matches the
refrigerant tubing and a nominal thickness of at least 0.5 inches;
(2) When testing split systems, if the indoor unit does not ship
with a cooling mode expansion device, test the system using the
device as specified in the installation instructions provided with
the indoor unit. If none is specified, test the system using a
thermostatic expansion valve with internal pressure equalization
that the valve manufacturer's product literature indicates is
appropriate for the system.
(3) When testing triple-split systems (see section 1.2,
Definitions), use the tubing length specified in section 6.1.3.5 of
AHRI 210/240-2008 (incorporated by reference, see Sec. 430.3) with
Addendum 1 and 2 to connect the outdoor coil, indoor compressor
section, and indoor coil while still meeting the requirement of
exposing 10 feet of the tubing to outside conditions; or
(4) When testing split systems having multiple indoor coils,
connect each indoor blower-coil to the outdoor unit using:
(a) 25 feet of tubing, or
(b) Tubing furnished by the manufacturer, whichever is longer.
If they are needed to make a secondary measurement of capacity,
install refrigerant pressure measuring instruments as described in
section 8.2.5 of ASHRAE Standard 37-2009(incorporated by reference,
see Sec. 430.3). Refer to section 2.10 of this appendix to learn
which secondary methods require refrigerant pressure measurements.
At a minimum, insulate the low-pressure line(s) of a split system
with insulation having an inside diameter that matches the
refrigerant tubing and a nominal thickness of 0.5 inch.
b. For units designed for both horizontal and vertical
installation or for both up-flow and down-flow vertical
installations, the manufacturer must use the orientation for testing
specified in the certification report. Conduct testing with the
following installed:
(1) The most restrictive filter(s);
(2) Supplementary heating coils; and
(3) Other equipment specified as part of the unit, including all
hardware used by a heat comfort controller if so equipped (see
section 1, Definitions). For small-duct, high-velocity systems,
configure all balance dampers or restrictor devices on or inside the
unit to fully open or lowest restriction.
c. Testing a ducted unit without having an indoor air filter
installed is permissible as long as the minimum external static
pressure requirement is adjusted as stated in Table 3, note 3 (see
section 3.1.4). Except as noted in section 3.1.10, prevent the
indoor air supplementary heating coils from operating during all
tests. For coil-only indoor units that are supplied without an
enclosure, create an enclosure using 1 inch fiberglass ductboard
having a nominal density of 6 pounds per cubic foot. Or
alternatively, use some other insulating material having a thermal
resistance (``R'' value) between 4 and 6 hr[middot]ft\2\[middot]
[deg]F/Btu. For units where the coil is housed within an enclosure
or cabinet, no extra insulating or sealing is allowed.
d. When testing oil-only central air conditioners and heat
pumps, install a toroidal-type transformer to power the system's
low-voltage components, complying with any additional requirements
for this transformer mentioned in the installation manuals included
with the unit by the manufacturer. If the installation manuals do
not provide specifications for the transformer, use a transformer
having the following features:
(1) A nominal volt-amp rating that results in the transformer
being loaded at a level that is between 25 and 90 percent based on
the highest power value expected and then confirmed during the off
mode test;
(2) Designed to operate with a primary input of 230 V, single
phase, 60 Hz; and
(3) That provides an output voltage that is within the specified
range for each low-voltage component. The power consumption of the
components connected to the transformer must be included as part of
the total system power consumption during the off mode tests, less
if included the power consumed by the transformer when no load is
connected to it.
e. An outdoor unit with no match (i.e., that is not sold with
indoor units) shall be tested without an indoor blower installed,
with a single cooling air volume rate, using an indoor unit whose
coil has (1) round tubes of outer diameter no less than 0.375
inches, and (2) a normalized gross indoor fin surface (NGIFS) no
greater than 1.15 square inches per British thermal unit per hour
(sq. in./Btu/hr). NGIFS is calculated as follows:
NGIFS = 2 x Lf x Wf x Nf / Qc(95)
Where,
Lf = Indoor coil fin length in inches, also height of the coil
transverse to the tubes.
Wf = Indoor coil fin width in inches, also depth of the coil.
Nf = Number of fins.
Qc(95) = the measured space cooling capacity of the tested
outdoor unit/indoor unit combination as determined from the A2 or A
Test whichever applies, Btu/h.
2.2.1 Defrost control settings.
Set heat pump defrost controls at the normal settings which most
typify those encountered in generalized climatic region IV. (Refer
to Figure 1 and Table 19 of section 4.2 for information on region
IV.) For heat pumps that use a time-adaptive defrost control system
(see section 1.2, Definitions), the manufacturer must specify the
frosting interval to be used during Frost Accumulation tests and
provide the procedure for manually initiating the defrost at the
specified time. To ease testing of any unit, the manufacturer should
provide information and any necessary hardware to manually initiate
a defrost cycle.
2.2.2 Special requirements for units having a multiple-speed
outdoor fan.
Configure the multiple-speed outdoor fan according to the
installation manual included with the unit by the manufacturer, and
thereafter, leave it unchanged for all tests. The controls of the
unit must regulate the operation of the outdoor fan during all lab
tests except dry coil cooling mode tests. For dry coil cooling mode
tests, the outdoor fan must operate at the same speed used during
the required wet coil test conducted at the same outdoor test
conditions.
2.2.3 Special requirements for multi-split air conditioners and
heat pumps, systems composed of multiple single-zone-multiple-coil
split-system units (having multiple outdoor units located side-by-
side), and ducted systems using a single indoor section containing
multiple blowers that would normally operate using two or more
indoor thermostats.
Because these systems will have more than one indoor blower and
possibly multiple outdoor fans and compressor systems, references in
this test procedure to a singular indoor blower, outdoor fan, and
compressor means all indoor blowers, all outdoor fans, and all
compressor systems that are energized during the test.
a. Additional requirements for multi-split air conditioners and
heat pumps and systems composed of multiple single-zone-multiple-
[[Page 69405]]
coil split-system units. For any test where the system is operated
at part load (i.e., one or more compressors ``off'', operating at
the intermediate or minimum compressor speed, or at low compressor
capacity), the manufacturer shall designate the indoor coil(s) that
are not providing heating or cooling during the test such that the
sum of the nominal heating or cooling capacity of the operational
indoor units is within 5 percent of the intended part load heating
or cooling capacity. For variable-speed systems, the manufacturer
must designate at least one indoor unit that is not providing
heating or cooling for all tests conducted at minimum compressor
speed. For all other part-load tests, the manufacturer shall choose
to turn off zero, one, two, or more indoor units. The chosen
configuration shall remain unchanged for all tests conducted at the
same compressor speed/capacity. For any indoor coil that is not
providing heating or cooling during a test, cease forced airflow
through this indoor coil and block its outlet duct.
b. Additional requirements for ducted systems with a single
indoor section containing multiple blowers where the blowers are
designed to cycle on and off independently of one another and are
not controlled such that all blowers are modulated to always operate
at the same air volume rate or speed. This Appendix covers systems
with a single-speed compressor or systems offering two fixed stages
of compressor capacity (e.g., a two-speed compressor, two single-
speed compressors). For any test where the system is operated at its
lowest capacity--i.e., the lowest total air volume rate allowed when
operating the single-speed compressor or when operating at low
compressor capacity--blowers accounting for at least one-third of
the full-load air volume rate must be turned off unless prevented by
the controls of the unit. In such cases, turn off as many blowers as
permitted by the unit's controls. Where more than one option exists
for meeting this ``off'' blower requirement, the manufacturer shall
include in its installation manuals included with the unit which
blower(s) are turned off. The chosen configuration shall remain
unchanged for all tests conducted at the same lowest capacity
configuration. For any indoor coil turned off during a test, cease
forced airflow through any outlet duct connected to an ``off''
blower.
c. For test setups where it is physically impossible for the
laboratory to use the required line length listed in Table 3 of
ANSI/AHRI Standard 1230-2010 (incorporated by reference, see Sec.
430.3) with Addendum 2, then the actual refrigerant line length used
by the laboratory may exceed the required length and the refrigerant
line length correction factors in Table 4 of ANSI/AHRI Standard
1230-2010 with Addendum 2 are applied.
2.2.4 Wet-bulb temperature requirements for the air entering the
indoor and outdoor coils.
2.2.4.1 Cooling mode tests.
For wet-coil cooling mode tests, regulate the water vapor
content of the air entering the indoor unit to the applicable wet-
bulb temperature listed in Tables 4 to 7. As noted in these same
tables, achieve a wet-bulb temperature during dry-coil cooling mode
tests that results in no condensate forming on the indoor coil.
Controlling the water vapor content of the air entering the outdoor
side of the unit is not required for cooling mode tests except when
testing:
(1) Units that reject condensate to the outdoor coil during wet
coil tests. Tables 4-7 list the applicable wet-bulb temperatures.
(2) Single-package units where all or part of the indoor section
is located in the outdoor test room. The average dew point
temperature of the air entering the outdoor coil during wet coil
tests must be within 3.0[emsp14][deg]F of the average
dew point temperature of the air entering the indoor coil over the
30-minute data collection interval described in section 3.3. For dry
coil tests on such units, it may be necessary to limit the moisture
content of the air entering the outdoor side of the unit to meet the
requirements of section 3.4.
2.2.4.2 Heating mode tests.
For heating mode tests, regulate the water vapor content of the
air entering the outdoor unit to the applicable wet-bulb temperature
listed in Tables 11 to 14. The wet-bulb temperature entering the
indoor side of the heat pump must not exceed 60[emsp14][deg]F.
Additionally, if the Outdoor Air Enthalpy test method is used while
testing a single-package heat pump where all or part of the outdoor
section is located in the indoor test room, adjust the wet-bulb
temperature for the air entering the indoor side to yield an indoor-
side dew point temperature that is as close as reasonably possible
to the dew point temperature of the outdoor-side entering air.
2.2.5 Additional refrigerant charging requirements.
2.2.5.1 The ``manufacturer's published instructions,'' as stated
in section 8.2 of ASHRAE Standard 37-2009 (incorporated by
reference, see Sec. 430.3) and ``manufacturer's installation
instructions'' discussed in this Appendix mean the manufacturer's
installation instructions that come packaged with or appear in the
labels applied to the unit. This does not include online manuals.
Installation instructions that are shipped with the unit shall take
precedence over installation instructions that appear in the labels
applied to the unit.
2.2.5.2 Instructions to Use for Charging
a. Where the manufacturer's installation instructions contain
two sets of refrigerant charging criteria, one for field
installations and one for lab testing, use the field installation
criteria.
b. For systems consisting of an outdoor unit manufacturer's
outdoor section and indoor section with differing charging
procedures the refrigerant charge shall be adjusted per the outdoor
installation instructions.
c. For systems consisting of an outdoor unit manufacturer's
outdoor section and an independent coil manufacturer's indoor
section with differing charging procedures the refrigerant charge
shall be adjusted per the indoor installation instructions.
2.2.5.3 Test(s) to Use for Charging
a. Use the tests or operating conditions specified in the
manufacturer's installation instructions for charging.
b. If the manufacturer's installation instructions do not
specify a test or operating conditions for charging or there are no
manufacturer's instructions, use the following test(s):
(1) For air conditioners or cooling and heating heat pumps, use
the A or A2 test.
(2) For cooling and heating heat pumps that do not function in
the H1 or H12 test with the charge set for the A or
A2 test and for heating-only heat pumps, use the H1 or
H12 test.
2.2.5.4 Parameters to Set and Their Target Values
a. Consult the manufacturer's installation instructions
regarding which parameters to set and their target values. If the
instructions provide ranges of values, select target values equal to
the midpoints of the provided ranges.
b. In the event of conflicting information between charging
instructions (defined as multiple conditions given for charge
adjustment where all conditions specified cannot be met), follow the
following hierarchy.
(1) For fixed orifice systems:
(i) Superheat
(ii) High side pressure or corresponding saturation or dew-point
temperature
(iii) Low side pressure or corresponding saturation or dew-point
temperature
(iv) Low side temperature
(v) High side temperature
(vi) Charge weight
(2) For expansion valve systems:
(i) Subcooling
(ii) High side pressure or corresponding saturation or dew-point
temperature
(iii) Low side pressure or corresponding saturation or dew-point
temperature
(iv) Approach temperature (difference between temperature of liquid
leaving condenser and condenser average inlet air temperature)
(v) Charge weight
c. If there are no installation instructions and/or they do not
provide parameters and target values, set superheat to a target
value of 12 [deg]F for fixed orifice systems or set subcooling to a
target value of 10 [deg]F for expansion valve systems.
2.2.5.5 Charging Tolerances
a. If the manufacturer's installation instructions specify
tolerances on target values for the charging parameters, set the
values using these tolerances.
b. Otherwise, use the following tolerances for the different
charging parameters:
1. Superheat: 2.0 [deg]F
2. Subcooling: 0.6 [deg]F
3. High side pressure or corresponding saturation or dew point
temperature: 4.0 psi or 1.0 [deg]F
4. Low side pressure or corresponding saturation or dew point
temperature: 2.0 psi or 0.8 [deg]F
5. High side temperature: 2.0 [deg]F
6. Low side temperature: 2.0 [deg]F
7. Approach temperature: 1.0 [deg]F
8. Charge weight: 2.0 ounce
2.2.5.6 Special Charging Instructions
a. Cooling and Heating Heat Pumps
If, using the initial charge set in the A or A2 test,
the conditions are not within the range specified in manufacturer's
instructions for the H1 or H12 test, make as
[[Page 69406]]
small as possible an adjustment to obtain conditions for this test
in the specified range. After this adjustment, recheck conditions in
the A or A2 test to confirm that they are still within
the specified range for this test.
b. Single-Package Systems
Unless otherwise directed by the manufacturer's installation
instructions, install one or more refrigerant line pressure gauges
during the setup of the unit if setting of refrigerant charge is
based on certain operating parameters:
(1) Install a pressure gauge on the liquid line if charging is
on the basis of subcooling, or high side pressure or corresponding
saturation or dew point temperature;
(2) Install a pressure gauge on the suction line if charging is
on the basis of superheat, or low side pressure or corresponding
saturation or dew point temperature. If manufacturer's installation
instructions indicate that pressure gauges are not to be installed,
setting of charge shall not be based on any of the parameters listed
in b.(1) and (2) of this section.
2.2.5.7 Near-azeotropic and zeotropic refrigerants.
Charging of near-azeotropic and zeotropic refrigerants shall
only be performed with refrigerant in the liquid state.
2.2.5.8 Adjustment of charge between tests.
After charging the system as described in this test procedure,
use the set refrigerant charge for all tests used to determine
performance. Do not adjust the refrigerant charge at any point
during testing.
2.3 Indoor air volume rates.
If a unit's controls allow for overspeeding the indoor blower
(usually on a temporary basis), take the necessary steps to prevent
overspeeding during all tests.
2.3.1 Cooling tests.
a. Set indoor blower airflow-control settings (e.g., fan motor
pin settings, fan motor speed) according to the installation
instructions that are provided with the equipment while meeting the
airflow requirements that are specified in section 3.1.4. If the
manufacturer installation instructions do not provide guidance on
the airflow-control settings for a system tested with the indoor
blower installed, select the lowest speed that will satisfy the
minimum external static pressure specified in section 3.1.4.1.1 with
an air volume rate at or higher than the rated full-load cooling air
volume rate while meeting the maximum air flow requirement.
b. Express the Cooling Full-load Air Volume Rate, the Cooling
Minimum Air Volume Rate, and the Cooling Intermediate Air Volume
Rate in terms of standard air.
2.3.2 Heating tests.
a. If needed, set the indoor blower airflow-control settings
(e.g., fan motor pin settings, fan motor speed) according to the
installation instructions that are provided with the equipment. Do
this set-up while meeting all applicable airflow requirements
specified in sections 3.1.4. For a cooling and heating heat pump
tested with an indoor blower installed, if the manufacturer
installation instructions do not provide guidance on the fan
airflow-control settings, use the same airflow-control settings used
for the cooling test. If the manufacturer installation instructions
do not provide guidance on the airflow-control settings for a
heating-only heat pump tested with the indoor blower installed,
select the lowest speed that will satisfy the minimum external
static pressure specified in section 3.1.4.4.3 with an air volume
rate at or higher than the rated heating full-load air volume rate.
b. Express the Heating Full-Load Air Volume Rate, the Heating
Minimum Air Volume Rate, the Heating Intermediate Air Volume Rate,
and the Heating Nominal Air Volume Rate in terms of standard air.
2.4 Indoor coil inlet and outlet duct connections.
Insulate and/or construct the outlet plenum described in section
2.4.1 and, if installed, the inlet plenum described in section 2.4.2
with thermal insulation having a nominal overall resistance (R-
value) of at least 19 hr[middot]ft\2\[middot] [deg]F/Btu.
2.4.1 Outlet plenum for the indoor unit.
a. Attach a plenum to the outlet of the indoor coil. (NOTE: for
some packaged systems, the indoor coil may be located in the outdoor
test room.)
b. For systems having multiple indoor coils, or multiple indoor
blowers within a single indoor section, attach a plenum to each
indoor coil or blower outlet. Connect two or more outlet plenums to
a single common duct so that each indoor coil ultimately connects to
an airflow measuring apparatus (section 2.6). If using more than one
indoor test room, do likewise, creating one or more common ducts
within each test room that contains multiple indoor coils. At the
plane where each plenum enters a common duct, install an adjustable
airflow damper and use it to equalize the static pressure in each
plenum. Each outlet air temperature grid (section 2.5.4) and airflow
measuring apparatus are located downstream of the inlet(s) to the
common duct.
c. For small-duct, high-velocity systems, install an outlet
plenum that has a diameter that is equal to or less than the value
listed below. The limit depends only on the Cooling Full-Load Air
Volume Rate (see section 3.1.4.1.1) and is effective regardless of
the flange dimensions on the outlet of the unit (or an air supply
plenum adapter accessory, if installed in accordance with the
manufacturer's installation instructions).
d. Add a static pressure tap to each face of the (each) outlet
plenum, if rectangular, or at four evenly distributed locations
along the circumference of an oval or round plenum. Create a
manifold that connects the four static pressure taps. Figures 7a,
7b, 7c of ASHRAE Standard 37-2009 (incorporated by reference, see
Sec. 430.3) shows two of the three options allowed for the manifold
configuration; the third option is the broken-ring, four-to-one
manifold configuration that is shown in Figure 7a of ASHRAE Standard
37-2009. See Figures 7a, 7b, 7c, and 8 of ASHRAE Standard 37-2009
for the cross-sectional dimensions and minimum length of the (each)
plenum and the locations for adding the static pressure taps for
units tested with and without an indoor blower installed.
Table 2--Size of Outlet Plenum
------------------------------------------------------------------------
Maximum
diameter * of
Cooling full-load air volume rate (scfm) outlet plenum
(inches)
------------------------------------------------------------------------
<=500................................................... 6
501 to 700.............................................. 7
701 to 900.............................................. 8
901 to 1100............................................. 9
1101 to 1400............................................ 10
1401 to 1750............................................ 11
------------------------------------------------------------------------
* If the outlet plenum is rectangular, calculate its equivalent diameter
using (4A/P,) where A is the cross-sectional area and P is the
perimeter of the rectangular plenum, and compare it to the listed
maximum diameter.
2.4.2 Inlet plenum for the indoor unit.
Install an inlet plenum when testing a coil-only indoor unit or
a packaged system where the indoor coil is located in the outdoor
test room. Add static pressure taps at the center of each face of
this plenum, if rectangular, or at four evenly distributed locations
along the circumference of an oval or round plenum. Make a manifold
that connects the four static-pressure taps using one of the three
configurations specified in section 2.4.1. See Figures 7b, 7c, and
Figure 8 of ASHRAE Standard 37-2009 (incorporated by reference, see
Sec. 430.3) for cross-sectional dimensions, the minimum length of
the inlet plenum, and the locations of the static-pressure taps.
When testing a ducted unit having an indoor blower (and the indoor
coil is in the indoor test room), test with an inlet plenum
installed unless physically prohibited by space limitations within
the test room. If used, construct the inlet plenum and add the four
static-pressure taps as shown in Figure 8 of ASHRAE Standard 37-
2009. If used, the inlet duct size shall equal the size of the inlet
opening of the air-handling (blower coil) unit or furnace, with a
minimum length of 6 inches. Manifold the four static-pressure taps
using one of the three configurations specified in section 2.4.1.d.
Never use an inlet plenum when testing a non-ducted system.
2.5 Indoor coil air property measurements and air damper box
applications.
Follow instructions for indoor coil air property measurements as
described in AHRI 210/240-Draft, appendix E, section E4, unless
otherwise instructed in this section.
a. Measure the dry-bulb temperature and water vapor content of
the air entering and leaving the indoor coil. If needed, use an air
sampling device to divert air to a sensor(s) that measures the water
vapor content of the air. See Section 5.3 of ASHRAE Standard 41.1-
2013 (incorporated by reference, see Sec. 430.3) for guidance on
constructing an air sampling device. No part of the air sampling
device or the tubing transferring the sampled air to the sensor
shall be within two inches of the test chamber floor, and the
transfer tubing shall be insulated. The sampling device may also
divert air to a remotely located sensor(s) that measures dry bulb
temperature. The air sampling device and the remotely located
temperature sensor(s) may be used to determine the entering air dry
bulb temperature during any test. The air
[[Page 69407]]
sampling device and the remotely located leaving air dry bulb
temperature sensor(s) may be used for all tests except:
(1) Cyclic tests; and
(2) Frost accumulation tests.
b. An acceptable alternative in all cases, including the two
special cases noted above, is to install a grid of dry bulb
temperature sensors within the outlet and inlet ducts. Use a
temperature grid to get the average dry bulb temperature at one
location, leaving or entering, or when two grids are applied as a
thermopile, to directly obtain the temperature difference. A grid of
temperature sensors (which may also be used for determining average
leaving air dry bulb temperature) is required to measure the
temperature distribution within a cross-section of the leaving
airstream.
c. Use an inlet and outlet air damper box, an inlet upturned
duct, or any combination thereof when conducting one or both of the
cyclic tests listed in sections 3.2 and 3.6 on ducted systems.
Otherwise if not conducting one or both of said cyclic tests,
install an outlet air damper box when testing ducted and non-ducted
heat pumps that cycle off the indoor blower during defrost cycles if
no other means is available for preventing natural or forced
convection through the indoor unit when the indoor blower is off.
Never use an inlet damper box or an inlet upturned duct when testing
a non-ducted system. An inlet upturned duct is a length of ductwork
so installed upstream from the inlet such that the indoor duct inlet
opening, facing upwards, is sufficiently high to prevent natural
convection transfer out of the duct. If an inlet upturned duct is
used, install a dry bulb temperature sensor near the inlet opening
of the indoor duct at a centerline location not higher than the
lowest elevation of the duct edges at the inlet, and ensure that the
variation of the dry bulb temperature at this location, measured at
least every minute during the compressor OFF period of the cyclic
test, does not exceed 1.0 [deg]F.
2.5.1 Test set-up on the inlet side of the indoor coil: For
cases where the inlet airflow prevention device is installed.
a. Install an airflow prevention device as specified in section
2.5.1.1 or 2.5.1.2, whichever applies.
b. For an inlet damper box, locate the grid of entering air dry-
bulb temperature sensors, if used, and the air sampling device, or
the sensor used to measure the water vapor content of the inlet air,
at a location immediately upstream of the damper box inlet. For an
inlet upturned duct, locate the grid of entering air dry-bulb
temperature sensors, if used, and the air sampling device, or the
sensor used to measure the water vapor content of the inlet air, at
a location at least one foot downstream from the beginning of the
insulated portion of the duct but before the static pressure
measurement; install a dry-bulb temperature sensor at a centerline
location not higher than the lowest elevation of the duct edges at
the device inlet.
2.5.1.1 If the section 2.4.2 inlet plenum is installed.
Construct the airflow prevention device having a cross-sectional
flow area equal to or greater than the flow area of the inlet
plenum. Install the airflow prevention device upstream of the inlet
plenum and construct ductwork connecting it to the inlet plenum. If
needed, use an adaptor plate or a transition duct section to connect
the airflow prevention device with the inlet plenum. Insulate the
ductwork and inlet plenum with thermal insulation that has a nominal
overall resistance (R-value) of at least 19 hr [middot] ft\2\
[middot] [deg]F/Btu.
2.5.1.2 If the section 2.4.2 inlet plenum is not installed.
Construct the airflow prevention device having a cross-sectional
flow area equal to or greater than the flow area of the air inlet of
the indoor unit. Install the airflow prevention device immediately
upstream of the inlet of the indoor unit. If needed, use an adaptor
plate or a short transition duct section to connect the airflow
prevention device with the unit's air inlet. Add static pressure
taps at the center of each face of a rectangular airflow prevention
device, or at four evenly distributed locations along the
circumference of an oval or round airflow prevention device. Locate
the pressure taps between the airflow prevention device and the
inlet of the indoor unit. Make a manifold that connects the four
static pressure taps. Insulate the ductwork with thermal insulation
that has a nominal overall resistance (R-value) of at least 19
hr[middot]ft\2\ [middot] [deg]F/Btu.
2.5.2 Test set-up on the inlet side of the indoor unit: For
cases where no airflow prevention device is installed.
If using the section 2.4.2 inlet plenum and a grid of dry bulb
temperature sensors, mount the grid at a location upstream of the
static pressure taps described in section 2.4.2, preferably at the
entrance plane of the inlet plenum. If the section 2.4.2 inlet
plenum is not used, but a grid of dry bulb temperature sensors is
used, locate the grid approximately 6 inches upstream from the inlet
of the indoor coil. Or, in the case of non-ducted units having
multiple indoor coils, locate a grid approximately 6 inches upstream
from the inlet of each indoor coil. Position an air sampling device,
or the sensor used to measure the water vapor content of the inlet
air, immediately upstream of the (each) entering air dry-bulb
temperature sensor grid. If a grid of sensors is not used, position
the entering air sampling device (or the sensor used to measure the
water vapor content of the inlet air) as if the grid were present.
2.5.3 Indoor coil static pressure difference measurement.
Section 6.5.2 of ASHRAE Standard 37-2009 describes the method
for fabricating static-pressure taps. Also refer to Figure 2A of
ASHRAE Standard 51-07/AMCA Standard 210-07 (incorporated by
reference, see Sec. 430.3). Use a differential pressure measuring
instrument that is accurate to within 0.01 inches of
water and has a resolution of at least 0.01 inches of water to
measure the static pressure difference between the indoor coil air
inlet and outlet. Connect one side of the differential pressure
instrument to the manifolded pressure taps installed in the outlet
plenum. Connect the other side of the instrument to the manifolded
pressure taps located in either the inlet plenum or incorporated
within the airflow prevention device. If an inlet plenum or inlet
airflow prevention device is not used, leave the inlet side of the
differential pressure instrument open to the surrounding atmosphere.
For non-ducted systems that are tested with multiple outlet plenums,
measure the static pressure within each outlet plenum relative to
the surrounding atmosphere.
2.5.4 Test set-up on the outlet side of the indoor coil.
a. Install an interconnecting duct between the outlet plenum
described in section 2.4.1 and the airflow measuring apparatus
described below in section 2.6. The cross-sectional flow area of the
interconnecting duct must be equal to or greater than the flow area
of the outlet plenum or the common duct used when testing non-ducted
units having multiple indoor coils. If needed, use adaptor plates or
transition duct sections to allow the connections. To minimize
leakage, tape joints within the interconnecting duct (and the outlet
plenum). Construct or insulate the entire flow section with thermal
insulation having a nominal overall resistance (R-value) of at least
19 hr[middot]ft\2\[middot] [deg]F/Btu.
b. Install a grid(s) of dry-bulb temperature sensors inside the
interconnecting duct. Also, install an air sampling device, or the
sensor(s) used to measure the water vapor content of the outlet air,
inside the interconnecting duct. Locate the dry-bulb temperature
grid(s) upstream of the air sampling device (or the in-duct
sensor(s) used to measure the water vapor content of the outlet
air). Air that circulates through an air sampling device and past a
remote water-vapor-content sensor(s) must be returned to the
interconnecting duct at a location:
(1) Downstream of the air sampling device;
(2) Upstream of the outlet air damper box, if installed; and
(3) Upstream of the section 2.6 airflow measuring apparatus.
2.5.4.1 Outlet air damper box placement and requirements.
If using an outlet air damper box (see section 2.5), install it
within the interconnecting duct at a location downstream of the
location where air from the sampling device is reintroduced or
downstream of the in-duct sensor that measures water vapor content
of the outlet air. The leakage rate from the combination of the
outlet plenum, the closed damper, and the duct section that connects
these two components must not exceed 20 cubic feet per minute when a
negative pressure of 1 inch of water column is maintained at the
plenum's inlet.
2.5.4.2 Procedures to minimize temperature maldistribution.
Use these procedures if necessary to correct temperature
maldistributions. Install a mixing device(s) upstream of the outlet
air, dry-bulb temperature grid (but downstream of the outlet plenum
static pressure taps). Use a perforated screen located between the
mixing device and the dry-bulb temperature grid, with a maximum open
area of 40 percent. One or both items should help to meet the
maximum outlet air temperature distribution specified in section
3.1.8. Mixing devices are described in sections 5.3.2 and 5.3.3 of
ASHRAE Standard 41.1-2013 (incorporated by reference, see Sec.
430.3) and
[[Page 69408]]
section 5.2.2 of ASHRAE Standard 41.2-87 (RA 92) (incorporated by
reference, see Sec. 430.3).
2.5.4.3 Minimizing air leakage.
For small-duct, high-velocity systems, install an air damper
near the end of the interconnecting duct, just prior to the
transition to the airflow measuring apparatus of section 2.6. To
minimize air leakage, adjust this damper such that the pressure in
the receiving chamber of the airflow measuring apparatus is no more
than 0.5 inch of water higher than the surrounding test room
ambient. If applicable, in lieu of installing a separate damper, use
the outlet air damper box of sections 2.5 and 2.5.4.1 if it allows
variable positioning. Also apply these steps to any conventional
indoor blower unit that creates a static pressure within the
receiving chamber of the airflow measuring apparatus that exceeds
the test room ambient pressure by more than 0.5 inches of water
column.
2.5.5 Dry bulb temperature measurement.
a. Measure dry bulb temperatures as specified in sections 4,
5.3, 6, 7.2, and 7.3 of ASHRAE Standard 41.1-2013 (incorporated by
reference, see Sec. 430.3).
b. Distribute the sensors of a dry-bulb temperature grid over
the entire flow area. The required minimum is 9 sensors per grid.
2.5.6 Water vapor content measurement.
Determine water vapor content by measuring dry-bulb temperature
combined with the air wet-bulb temperature, dew point temperature,
or relative humidity. If used, construct and apply wet-bulb
temperature sensors as specified in sections 4, 5, 6, 7.2, 7.3, 7.4,
and 7.5 of ASHRAE Standard 41.6-2014 (incorporated by reference, see
Sec. 430.3). The temperature sensor (wick removed) must be accurate
to within 0.2 [deg]F. If used, apply dew point
hygrometers as specified in sections 4, 5, 6, and 7.1 of ASHRAE
Standard 41.6-2014. The dew point hygrometers must be accurate to
within 0.4 [deg]F when operated at conditions that
result in the evaluation of dew points above 35 [deg]F. If used, a
relative humidity (RH) meter must be accurate to within 0.7% RH. Other means to determine the psychrometric state of
air may be used as long as the measurement accuracy is equivalent to
or better than the accuracy achieved from using a wet-bulb
temperature sensor that meets the above specifications.
2.5.7 Air damper box performance requirements.
If used (see section 2.5), the air damper box(es) must be
capable of being completely opened or completely closed within 10
seconds for each action.
2.6 Airflow measuring apparatus.
a. Fabricate and operate an Air Flow Measuring Apparatus as
specified in section 6.2 and 6.3 of ASHRAE Standard 37-2009. Refer
to Figure 12 of ASHRAE Standard 51-07/AMCA Standard 210-07 or Figure
14 of ASHRAE Standard 41.2-87 (RA 92) (incorporated by reference,
see Sec. 430.3) for guidance on placing the static pressure taps
and positioning the diffusion baffle (settling means) relative to
the chamber inlet. When measuring the static pressure difference
across nozzles and/or velocity pressure at nozzle throats using
electronic pressure transducers and a data acquisition system, if
high frequency fluctuations cause measurement variations to exceed
the test tolerance limits specified in section 9.2 and Table 2 of
ASHRAE Standard 37-2009, dampen the measurement system such that the
time constant associated with response to a step change in
measurement (time for the response to change 63% of the way from the
initial output to the final output) is no longer than five seconds.
b. Connect the airflow measuring apparatus to the
interconnecting duct section described in section 2.5.4. See
sections 6.1.1, 6.1.2, and 6.1.4, and Figures 1, 2, and 4 of ASHRAE
Standard 37-2009; and Figures D1, D2, and D4 of AHRI 210/240-2008
(incorporated by reference, see Sec. 430.3) with Addendum 1 and 2
for illustrative examples of how the test apparatus may be applied
within a complete laboratory set-up. Instead of following one of
these examples, an alternative set-up may be used to handle the air
leaving the airflow measuring apparatus and to supply properly
conditioned air to the test unit's inlet. The alternative set-up,
however, must not interfere with the prescribed means for measuring
airflow rate, inlet and outlet air temperatures, inlet and outlet
water vapor contents, and external static pressures, nor create
abnormal conditions surrounding the test unit. (Note: Do not use an
enclosure as described in section 6.1.3 of ASHRAE Standard 37-2009
when testing triple-split units.)
2.7 Electrical voltage supply.
Perform all tests at the voltage specified in section 6.1.3.2 of
AHRI 210/240-2008 with Addendum 1 and 2 for ``Standard Rating
Tests.'' If the voltage on the nameplate of indoor and outdoor units
differs, the voltage supply on the outdoor unit shall be selected
for testing. Measure the supply voltage at the terminals on the test
unit using a volt meter that provides a reading that is accurate to
within 1.0 percent of the measured quantity.
2.8 Electrical power and energy measurements.
a. Use an integrating power (watt-hour) measuring system to
determine the electrical energy or average electrical power supplied
to all components of the air conditioner or heat pump (including
auxiliary components such as controls, transformers, crankcase
heater, integral condensate pump on non-ducted indoor units, etc.).
The watt-hour measuring system must give readings that are accurate
to within 0.5 percent. For cyclic tests, this accuracy
is required during both the ON and OFF cycles. Use either two
different scales on the same watt-hour meter or two separate watt-
hour meters. Activate the scale or meter having the lower power
rating within 15 seconds after beginning an OFF cycle. Activate the
scale or meter having the higher power rating active within 15
seconds prior to beginning an ON cycle. For ducted units tested with
a fan installed, the ON cycle lasts from compressor ON to indoor
blower OFF. For ducted units tested without an indoor blower
installed, the ON cycle lasts from compressor ON to compressor OFF.
For non-ducted units, the ON cycle lasts from indoor blower ON to
indoor blower OFF. When testing air conditioners and heat pumps
having a variable-speed compressor, avoid using an induction watt/
watt-hour meter.
b. When performing section 3.5 and/or 3.8 cyclic tests on non-
ducted units, provide instrumentation to determine the average
electrical power consumption of the indoor blower motor to within
1.0 percent. If required according to sections 3.3, 3.4,
3.7, 3.9.1, and/or 3.10, this same instrumentation requirement
applies when testing air conditioners and heat pumps having a
variable-speed constant-air-volume-rate indoor blower or a variable-
speed, variable-air-volume-rate indoor blower.
2.9 Time measurements.
Make elapsed time measurements using an instrument that yields
readings accurate to within 0.2 percent.
2.10 Test apparatus for the secondary space conditioning
capacity measurement.
For all tests, use the Indoor Air Enthalpy Method to measure the
unit's capacity. This method uses the test set-up specified in
sections 2.4 to 2.6. In addition, for all steady-state tests,
conduct a second, independent measurement of capacity as described
in section 3.1.1. For split systems, use one of the following
secondary measurement methods: Outdoor Air Enthalpy Method,
Compressor Calibration Method, or Refrigerant Enthalpy Method. For
single-package units, use either the Outdoor Air Enthalpy Method or
the Compressor Calibration Method as the secondary measurement.
2.10.1 Outdoor Air Enthalpy Method.
a. To make a secondary measurement of indoor space conditioning
capacity using the Outdoor Air Enthalpy Method, do the following:
(1) Measure the electrical power consumption of the test unit;
(2) Measure the air-side capacity at the outdoor coil; and
(3) Apply a heat balance on the refrigerant cycle.
b. The test apparatus required for the Outdoor Air Enthalpy
Method is a subset of the apparatus used for the Indoor Air Enthalpy
Method. Required apparatus includes the following:
(1) On the outlet side, an outlet plenum containing static
pressure taps (sections 2.4, 2.4.1, and 2.5.3),
(2) An airflow measuring apparatus (section 2.6),
(3) A duct section that connects these two components and itself
contains the instrumentation for measuring the dry-bulb temperature
and water vapor content of the air leaving the outdoor coil
(sections 2.5.4, 2.5.5, and 2.5.6), and
(4) On the inlet side, a sampling device and temperature grid
(section 2.11b.).
c. During the preliminary tests described in sections 3.11.1 and
3.11.1.1, measure the evaporator and condenser temperatures or
pressures. On both the outdoor coil and the indoor coil, solder a
thermocouple onto a return bend located at or near the midpoint of
each coil or at points not affected by vapor superheat or liquid
subcooling. Alternatively, if the test unit is not sensitive to the
refrigerant charge, install pressure gages to the access valves or
to ports created from tapping into the suction and discharge lines
according to sections 7.4.2 and 8.2.5 of ASHRAE Standard 37-2009.
Use this
[[Page 69409]]
alternative approach when testing a unit charged with a zeotropic
refrigerant having a temperature glide in excess of 1 [deg]F at the
specified test conditions.
2.10.2 Compressor Calibration Method.
Measure refrigerant pressures and temperatures to determine the
evaporator superheat and the enthalpy of the refrigerant that enters
and exits the indoor coil. Determine refrigerant flow rate or, when
the superheat of the refrigerant leaving the evaporator is less than
5 [deg]F, total capacity from separate calibration tests conducted
under identical operating conditions. When using this method,
install instrumentation, measure refrigerant properties, and adjust
the refrigerant charge according to section 7.4.2 and 8.2.5 of
ASHRAE Standard 37-2009 (incorporated by reference, see Sec.
430.3). Use refrigerant temperature and pressure measuring
instruments that meet the specifications given in sections 5.1.1 and
5.2 of ASHRAE Standard 37-2009.
2.10.3 Refrigerant Enthalpy Method.
For this method, calculate space conditioning capacity by
determining the refrigerant enthalpy change for the indoor coil and
directly measuring the refrigerant flow rate. Use section 7.5.2 of
ASHRAE Standard 37-2009 for the requirements for this method,
including the additional instrumentation requirements, and
information on placing the flow meter and a sight glass. Use
refrigerant temperature, pressure, and flow measuring instruments
that meet the specifications given in sections 5.1.1, 5.2, and 5.5.1
of ASHRAE Standard 37-2009. Refrigerant flow measurement device(s),
if used, must be elevated at least two feet from the test chamber
floor or placed upon insulating material having a total thermal
resistance of at least R-12 and extending at least one foot
laterally beyond each side of the device(s)' exposed surfaces,
unless the device(s) are elevated at least two feet from the floor.
2.11 Measurement of test room ambient conditions.
Follow instructions for measurement of test room ambient
conditions as described in AHRI 210/240-Draft, appendix E, section
E4, (incorporated by reference, see Sec. 430.3) unless otherwise
instructed in this section.
a. If using a test set-up where air is ducted directly from the
conditioning apparatus to the indoor coil inlet (see Figure 2, Loop
Air-Enthalpy Test Method Arrangement, of ASHRAE Standard 37-2009),
add instrumentation to permit measurement of the indoor test room
dry-bulb temperature.
b. For the outdoor side, install a grid of evenly-distributed
sensors on every air-permitting face on the inlet of the outdoor
unit, such that each measurement represents an air-inlet area of no
more than one square foot. This grid must be constructed and applied
as per section 5.3 of ASHRAE Standard 41.1-2013 (incorporated by
reference, see Sec. 430.3). The maximum and minimum temperatures
measured by these sensors may differ by no more than 1.5 [deg]F--
otherwise adjustments to the test room must be made to improve
temperature uniformity. The outdoor conditions shall be verified
with the air collected by air sampling device. Air collected by an
air sampling device at the air inlet of the outdoor unit for
transfer to sensors for measurement of temperature and/or humidity
shall be protected from temperature change as follows: Any surface
of the air conveying tubing in contact with surrounding air at a
different temperature than the sampled air shall be insulated with
thermal insulation with a nominal thermal resistance (R-value) of at
least 19 hr [middot] ft\2\ [middot] [deg]F/Btu, no part of the air
sampling device or the tubing conducting the sampled air to the
sensors shall be within two inches of the test chamber floor, and
pairs of measurements (e.g. dry bulb temperature and wet bulb
temperature) used to determine water vapor content of sampled air
shall be measured in the same location. Take steps (e.g., add or re-
position a lab circulating fan), as needed, to maximize temperature
uniformity within the outdoor test room. However, ensure that any
fan used for this purpose does not cause air velocities in the
vicinity of the test unit to exceed 500 feet per minute.
c. Measure dry bulb temperatures as specified in sections 4, 5,
7.2, 6, and 7.3 of ASHRAE Standard 41.1-2013. Measure water vapor
content as stated above in section 2.5.6.
2.12 Measurement of indoor blower speed.
When required, measure fan speed using a revolution counter,
tachometer, or stroboscope that gives readings accurate to within
1.0 percent.
2.13 Measurement of barometric pressure.
Determine the average barometric pressure during each test. Use
an instrument that meets the requirements specified in section 5.2
of ASHRAE Standard 37-2009.
3. Testing Procedures.
3.1 General Requirements.
If, during the testing process, an equipment set-up adjustment
is made that would have altered the performance of the unit during
any already completed test, then repeat all tests affected by the
adjustment. For cyclic tests, instead of maintaining an air volume
rate, for each airflow nozzle, maintain the static pressure
difference or velocity pressure during an ON period at the same
pressure difference or velocity pressure as measured during the
steady-state test conducted at the same test conditions.
Use the testing procedures in this section to collect the data
used for calculating
(1) Performance metrics for central air conditioners and heat
pumps during the cooling season;
(2) Performance metrics for heat pumps during the heating
season; and
(3) Power consumption metric(s) for central air conditioners and
heat pumps during the off mode season(s).
3.1.1 Primary and secondary test methods.
For all tests, use the Indoor Air Enthalpy Method test apparatus
to determine the unit's space conditioning capacity. The procedure
and data collected, however, differ slightly depending upon whether
the test is a steady-state test, a cyclic test, or a Frost
Accumulation test. The following sections described these
differences. For all steady-state tests (i.e., the A, A2,
A1, B, B2, B1, C, C1,
EV, F1, G1, H01, H1,
H12, H11, HIN, H3,
H32, and H31 Tests), in addition, use one of
the acceptable secondary methods specified in section 2.10 to
determine indoor space conditioning capacity. Calculate this
secondary check of capacity according to section 3.11. The two
capacity measurements must agree to within 6 percent to constitute a
valid test. For this capacity comparison, use the Indoor Air
Enthalpy Method capacity that is calculated in section 7.3 of ASHRAE
Standard 37-2009 (and, if testing a coil-only system, do not make
the after-test fan heat adjustments described in section 3.3, 3.4,
3.7, and 3.10 of this appendix). However, include the appropriate
section 3.3 to 3.5 and 3.7 to 3.10 fan heat adjustments within the
Indoor Air Enthalpy Method capacities used for the section 4
seasonal calculations.
3.1.2 Manufacturer-provided equipment overrides.
Where needed, the manufacturer must provide a means for
overriding the controls of the test unit so that the compressor(s)
operates at the specified speed or capacity and the indoor blower
operates at the specified speed or delivers the specified air volume
rate.
3.1.3 Airflow through the outdoor coil.
For all tests, meet the requirements given in section 6.1.3.4 of
AHRI 210/240-2008 (incorporated by reference, see Sec. 430.3) with
Addendum 1 and 2 when obtaining the airflow through the outdoor
coil.
3.1.3.1 Double-ducted.
For products intended to be installed with the outdoor airflow
ducted, the unit shall be installed with outdoor coil ductwork
installed per manufacturer installation instructions and shall
operate between 0.10 and 0.15 in H2O external static
pressure. External static pressure measurements shall be made in
accordance with ASHRAE Standard 37-2009 Section 6.4 and 6.5.
3.1.4 Airflow through the indoor coil.
Airflow setting(s) shall be determined before testing begins.
Unless otherwise specified within this or its subsections, no
changes shall be made to the airflow setting(s) after initiation of
testing.
3.1.4.1 Cooling Full-load Air Volume Rate.
3.1.4.1.1 Cooling Full-Load Air Volume Rate for Ducted Units.
The manufacturer must specify the cooling full-load air volume
rate and the instructions for setting fan speed or controls. Adjust
the cooling full-load air volume rate if needed to satisfy the
additional requirements of this section. First, when conducting the
A or A2 Test (exclusively), the measured air volume rate,
when divided by the measured indoor air-side total cooling capacity
must not exceed 37.5 cubic feet per minute of standard air (scfm)
per 1000 Btu/h. If this ratio is exceeded, reduce the air volume
rate until this ratio is equaled. Use this reduced air volume rate
for all tests that call for using the Cooling Full-load Air Volume
Rate. Pressure requirements are as follows:
a. For all ducted units tested with an indoor blower installed,
except those having a constant-air-volume-rate indoor blower:
1. Achieve the Cooling Full-load Air Volume Rate, determined in
accordance with the previous paragraph;
2. Measure the external static pressure;
[[Page 69410]]
3. If this pressure is equal to or greater than the applicable
minimum external static pressure cited in Table 3, the pressure
requirement is satisfied. Use the current air volume rate for all
tests that require the Cooling Full-load Air Volume Rate.
4. If the Table 3 minimum is not equaled or exceeded,
4a. reduce the air volume rate and increase the external static
pressure by adjusting the exhaust fan of the airflow measuring
apparatus until the applicable Table 3 minimum is equaled or
4b. until the measured air volume rate equals 90 percent of the
air volume rate from step 1, whichever occurs first.
5. If the conditions of step 4a occur first, the pressure
requirement is satisfied. Use the step 4a reduced air volume rate
for all tests that require the Cooling Full-load Air Volume Rate.
6. If the conditions of step 4b occur first, make an incremental
change to the set-up of the indoor blower (e.g., next highest fan
motor pin setting, next highest fan motor speed) and repeat the
evaluation process beginning at above step 1. If the indoor blower
set-up cannot be further changed, reduce the air volume rate and
increase the external static pressure by adjusting the exhaust fan
of the airflow measuring apparatus until the applicable Table 3
minimum is equaled. Use this reduced air volume rate for all tests
that require the Cooling Full-load Air Volume Rate.
b. For ducted units that are tested with a constant-air-volume-
rate indoor blower installed. For all tests that specify the Cooling
Full-load Air Volume Rate, obtain an external static pressure as
close to (but not less than) the applicable Table 3 value that does
not cause automatic shutdown of the indoor blower or air volume rate
variation QVar, defined as follows, greater than 10
percent.
[GRAPHIC] [TIFF OMITTED] TP09NO15.220
Where,
Qmax = maximum measured airflow value
Qmin = minimum measured airflow value
QVar = airflow variance, percent
Additional test steps as described in section 3.3.(e) of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For ducted units that are tested without an indoor blower
installed. For the A or A2 Test, (exclusively), the
pressure drop across the indoor coil assembly must not exceed 0.30
inches of water. If this pressure drop is exceeded, reduce the air
volume rate until the measured pressure drop equals the specified
maximum. Use this reduced air volume rate for all tests that require
the Cooling Full-load Air Volume Rate.
Table 3--Minimum External Static Pressure for Ducted Systems Tested With an Indoor Blower Installed
----------------------------------------------------------------------------------------------------------------
Minimum external static pressure \3\ (Inches
of water)
-----------------------------------------------
Rated Cooling \1\ or heating \2\ capacity (Btu/h) Small-duct,
Short ducted high-velocity All other
systems \6\ systems 4 5 systems
----------------------------------------------------------------------------------------------------------------
<=28,800........................................................ 0.03 1.10 0.45
>=29,000 and <=42,500........................................... 0.05 1.15 0.50
>=43,000........................................................ 0.07 1.20 0.55
----------------------------------------------------------------------------------------------------------------
\1\ For air conditioners and heat pumps, the value cited by the manufacturer in published literature for the
unit's capacity when operated at the A or A2 Test conditions.
\2\ For heating-only heat pumps, the value the manufacturer cites in published literature for the unit's
capacity when operated at the H1 or H12 Test conditions.
\3\ For ducted units tested without an air filter installed, increase the applicable tabular value by 0.08
inches of water. For ducted units for which the indoor blower installed for testing is the fan of a condensing
gas furnace, decrease the applicable tabular value by 0.10 inches of water (make both adjustments if they both
apply). If the adjusted value is less than zero, readjust it to zero.
\4\ See section 1.2, Definitions, to determine if the equipment qualifies as a small-duct, high-velocity system.
\5\ If a closed-loop, air-enthalpy test apparatus is used on the indoor side, limit the resistance to airflow on
the inlet side of the indoor blower coil to a maximum value of 0.1 inch of water. Impose the balance of the
airflow resistance on the outlet side of the indoor blower.
\6\ See section 1.2. Definitions.
d. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the full-load air volume rate with all
blowers operating unless prevented by the controls of the unit. In
such cases, turn on the maximum number of blowers permitted by the
unit's controls. Where more than one option exists for meeting this
``on'' blower requirement, which blower(s) are turned on must match
that specified by the manufacturer in the installation manuals
included with the unit. Conduct section 3.1.4.1.1 setup steps for
each blower separately. If two or more indoor blowers are connected
to a common duct as per section 2.4.1, either turn off the other
indoor blowers connected to the same common duct or temporarily
divert their air volume to the test room when confirming or
adjusting the setup configuration of individual blowers. If the
indoor blowers are all the same size or model, the target air volume
rate for each blower plenum equals the full-load air volume rate
divided by the number of ``on'' blowers. If different size blowers
are used within the indoor section, the allocation of the system's
full-load air volume rate assigned to each ``on'' blower must match
that specified by the manufacturer in the installation manuals
included with the unit.
3.1.4.1.2 Cooling Full-load Air Volume Rate for Non-ducted
Units.
For non-ducted units, the Cooling Full-load Air Volume Rate is
the air volume rate that results during each test when the unit is
operated at an external static pressure of zero inches of water.
3.1.4.2 Cooling Minimum Air Volume Rate.
The manufacturer must specify the cooling minimum air volume
rate and the instructions for setting fan speed or controls. The
target external static pressure, [Delta]Pst_i, for any
test ``i'' with a specified air volume rate not equal to the cooling
full-load air volume rate is determined as follows.
[[Page 69411]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.221
Where:
[Delta]Pst_i = target minimum external static pressure
for test i;
[Delta]Pst_full = minimum external static pressure for
test A or A2 (Table 3);
Qi = air volume rate for test i; and
Qfull = cooling full-load air volume rate as measured
after setting and/or adjustment as described in section 3.1.4.1.1.
a. For ducted units tested with an indoor blower installed that
is not a constant-air-volume indoor blower, adjust for external
static pressure as follows.
1. Achieve the manufacturer-specified cooling minimum air volume
rate;
2. Measure the external static pressure;
3. If this pressure is equal to or greater than the target
minimum external static pressure calculated as described above, use
the current air volume rate for all tests that require the cooling
minimum air volume rate.
4. If the target minimum is not equaled or exceeded,
4a. reduce the air volume rate and increase the external static
pressure by adjusting the exhaust fan of the airflow measuring
apparatus until the applicable target minimum is equaled or
4b. until the measured air volume rate equals 90 percent of the
air volume rate from step 1, whichever occurs first.
5. If the conditions of step 4a occur first, use the step 4a
reduced air volume rate for all tests that require the cooling
minimum air volume rate.
6. If the conditions of step 4b occur first, make an incremental
change to the set-up of the indoor fan (e.g., next highest fan motor
pin setting, next highest fan motor speed) and repeat the evaluation
process beginning at above step 1. If the indoor fan set-up cannot
be further changed, reduce the air volume rate and increase the
external static pressure by adjusting the exhaust fan of the airflow
measuring apparatus until the applicable target minimum is equaled.
Use this reduced air volume rate for all tests that require the
cooling minimum air volume rate.
b. For ducted units with constant-air-volume indoor blowers,
conduct all tests that specify the cooling minimum air volume rate--
(i.e., the A1, B1, C1,
F1, and G1 Tests)--at an external static
pressure that does not cause an automatic shutdown of the indoor
blower or air volume rate variation QVar, defined in
section 3.1.4.1.1.b, greater than 10 percent, while being as close
to, but not less than the target minimum external static pressure.
Additional test steps as described in section 3.3(e) of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For ducted two-capacity units that are tested without an
indoor blower installed, the Cooling Minimum Air Volume Rate is the
higher of (1) the rate specified by the installation instructions
included with the unit by the manufacturer or (2) 75 percent of the
Cooling Full-load Air Volume Rate. During the laboratory tests on a
coil-only (fanless) unit, obtain this Cooling Minimum Air Volume
Rate regardless of the pressure drop across the indoor coil
assembly.
d. For non-ducted units, the Cooling Minimum Air Volume Rate is
the air volume rate that results during each test when the unit
operates at an external static pressure of zero inches of water and
at the indoor fan setting used at low compressor capacity (two-
capacity system) or minimum compressor speed (variable-speed
system). For units having a single-speed compressor and a variable-
speed variable-air-volume-rate indoor fan, use the lowest fan
setting allowed for cooling.
e. For ducted systems having multiple indoor blowers within a
single indoor section, operate the indoor blowers such that the
lowest air volume rate allowed by the unit's controls is obtained
when operating the lone single-speed compressor or when operating at
low compressor capacity while meeting the requirements of section
2.2.3.2 for the minimum number of blowers that must be turned off.
Adjust for external static pressure and if necessary adjust air
volume rates as described in section 3.1.4.2.a if the indoor fan is
not a constant-air-volume indoor fan or as described in section
3.1.4.2.b if the indoor fan is a constant-air-volume indoor fan. The
sum of the individual ``on'' blowers' air volume rates is the
cooling minimum air volume rate for the system.
3.1.4.3 Cooling Intermediate Air Volume Rate.
The manufacturer must specify the cooling intermediate air
volume rate and the instructions for setting fan speed or controls.
Calculate target minimum external static pressure as described in
section 3.1.4.2.
a. For ducted units tested with an indoor blower, installed that
is not a constant-air-volume indoor blower, adjust for external
static pressure as described in section 3.1.4.2.a for cooling
minimum air volume rate.
b. For ducted units tested with constant-air-volume indoor
blowers installed, conduct the EV Test at an external
static pressure that does not cause an automatic shutdown of the
indoor blower or air volume rate variation QVar, defined
in section 3.1.4.1.1.b, greater than 10 percent, while being as
close to, but not less than the target minimum external static
pressure. Additional test steps as described in section 3.3(e) of
this appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For non-ducted units, the Cooling Intermediate Air Volume
Rate is the air volume rate that results when the unit operates at
an external static pressure of zero inches of water and at the fan
speed selected by the controls of the unit for the EV
Test conditions.
3.1.4.4 Heating Full-load Air Volume Rate.
3.1.4.4.1 Ducted heat pumps where the Heating and Cooling Full-
load Air Volume Rates are the same.
a. Use the Cooling Full-load Air Volume Rate as the Heating
Full-load Air Volume Rate for:
1. Ducted heat pumps tested with an indoor blower installed that
is not a constant-air-volume indoor blower that operates at the same
airflow-control setting during both the A (or A2) and the
H1 (or H12) Tests;
2. Ducted heat pumps tested with constant-air-flow indoor
blowers installed that provide the same air flow for the A (or
A2) and the H1 (or H12) Tests; and
3. Ducted heat pumps that are tested without an indoor blower
installed (except two-capacity northern heat pumps that are tested
only at low capacity cooling--see 3.1.4.4.2).
b. For heat pumps that meet the above criteria ``1'' and ``3,''
no minimum requirements apply to the measured external or internal,
respectively, static pressure. For heat pumps that meet the above
criterion ``2,'' test at an external static pressure that does not
cause an automatic shutdown of the indoor blower or air volume rate
variation QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but not less than, the
same Table 3 minimum external static pressure as was specified for
the A (or A2) cooling mode test. Additional test steps as
described in section 3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the target value by more
than 0.03 inches of water.
3.1.4.4.2 Ducted heat pumps where the Heating and Cooling Full-
load Air Volume Rates are different due to indoor blower operation.
The manufacturer must specify the heating full-load air volume
rate and the instructions for setting fan speed or controls.
Calculate target minimum external static pressure as described in
section 3.1.4.2.
a. For ducted heat pumps tested with an indoor blower installed
that is not a constant-air-volume indoor blower, adjust for external
static pressure as described in section 3.1.4.2.a for cooling
minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct all tests that specify the heating full-
load air volume rate at an external static pressure that does not
cause an automatic shutdown of the indoor blower or air volume rate
variation QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but not less than the
target minimum external static pressure. Additional test steps as
described in section 3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the target value by more
than 0.03 inches of water.
[[Page 69412]]
c. When testing ducted, two-capacity northern heat pumps (see
section 1.2, Definitions), use the appropriate approach of the above
two cases for units that are tested with an indoor blower installed.
For coil-only northern heat pumps, the Heating Full-load Air Volume
Rate is the lesser of the rate specified by the manufacturer in the
installation instructions included with the unit or 133 percent of
the Cooling Full-load Air Volume Rate. For this latter case, obtain
the Heating Full-load Air Volume Rate regardless of the pressure
drop across the indoor coil assembly.
d. For ducted systems having multiple indoor blowers within a
single indoor section, obtain the heating full-load air volume rate
using the same ``on'' blowers as used for the cooling full-load air
volume rate. For systems where individual blowers regulate the speed
(as opposed to the cfm) of the indoor blower, use the first section
3.1.4.2 equation for each blower individually. Sum the individual
blower air volume rates to obtain the heating full-load air volume
rate for the system.
3.1.4.4.3 Ducted heating-only heat pumps.
The manufacturer must specify the Heating Full-load Air Volume
Rate.
a. For all ducted heating-only heat pumps tested with an indoor
blower installed, except those having a constant-air-volume-rate
indoor blower. Conduct the following steps only during the first
test, the H1 or H12 Test.
1. Achieve the Heating Full-load Air Volume Rate.
2. Measure the external static pressure.
3. If this pressure is equal to or greater than the Table 3
minimum external static pressure that applies given the heating-only
heat pump's rated heating capacity, use the current air volume rate
for all tests that require the Heating Full-load Air Volume Rate.
4. If the Table 3 minimum is not equaled or exceeded,
4a. reduce the air volume rate and increase the external static
pressure by adjusting the exhaust fan of the airflow measuring
apparatus until the applicable Table 3 minimum is equaled or
4b. until the measured air volume rate equals 90 percent of the
manufacturer-specified Full-load Air Volume Rate, whichever occurs
first.
5. If the conditions of step 4a occurs first, use the step 4a
reduced air volume rate for all tests that require the Heating Full-
load Air Volume Rate.
6. If the conditions of step 4b occur first, make an incremental
change to the set-up of the indoor blower (e.g., next highest fan
motor pin setting, next highest fan motor speed) and repeat the
evaluation process beginning at above step 1. If the indoor blower
set-up cannot be further changed, reduce the air volume rate until
the applicable Table 3 minimum is equaled. Use this reduced air
volume rate for all tests that require the Heating Full-load Air
Volume Rate.
b. For ducted heating-only heat pumps that are tested with a
constant-air-volume-rate indoor blower installed. For all tests that
specify the Heating Full-load Air Volume Rate, obtain an external
static pressure that does not cause an automatic shutdown of the
indoor blower or air volume rate variation QVar, defined
in section 3.1.4.1.1.b, greater than 10 percent, while being as
close to, but not less than, the applicable Table 3 minimum.
Additional test steps as described in section 3.9.1(c) of this
appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For ducted heating-only heat pumps that are tested without an
indoor blower installed. For the H1 or H12 Test,
(exclusively), the pressure drop across the indoor coil assembly
must not exceed 0.30 inches of water. If this pressure drop is
exceeded, reduce the air volume rate until the measured pressure
drop equals the specified maximum. Use this reduced air volume rate
for all tests that require the Heating Full-load Air Volume Rate.
3.1.4.4.4 Non-ducted heat pumps, including non-ducted heating-
only heat pumps.
For non-ducted heat pumps, the Heating Full-load Air Volume Rate
is the air volume rate that results during each test when the unit
operates at an external static pressure of zero inches of water.
3.1.4.5 Heating Minimum Air Volume Rate.
3.1.4.5.1 Ducted heat pumps where the Heating and Cooling
Minimum Air Volume Rates are the same.
a. Use the Cooling Minimum Air Volume Rate as the Heating
Minimum Air Volume Rate for:
1. Ducted heat pumps tested with an indoor blower installed that
is not a constant-air-volume indoor blower that operates at the same
airflow-control setting during both the A1 and the
H11 tests; 2. Ducted heat pumps tested with constant-air-
flow indoor blowers installed that provide the same air flow for the
A1 and the H11 Tests; and
3. Ducted heat pumps that are tested without an indoor blower
installed (except two-capacity northern heat pumps that are tested
only at low capacity cooling--see 3.1.4.4.2).
b. For heat pumps that meet the above criteria ``1'' and ``3,''
no minimum requirements apply to the measured external or internal,
respectively, static pressure. For heat pumps that meet the above
criterion ``2,'' test at an external static pressure that does not
cause an automatic shutdown of the indoor blower or air volume rate
variation QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but not less than, the
same target minimum external static pressure as was specified for
the A1 cooling mode test. Additional test steps as
described in section 3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the target value by more
than 0.03 inches of water.
3.1.4.5.2 Ducted heat pumps where the Heating and Cooling
Minimum Air Volume Rates are different due to indoor blower
operation.
The manufacturer must specify the heating minimum volume rate
and the instructions for setting fan speed or controls. Calculate
target minimum external static pressure as described in section
3.1.4.2.
a. For ducted heat pumps tested with an indoor blower installed
that is not a constant-air-volume indoor blower, adjust for external
static pressure as described in section 3.1.4.2.a for cooling
minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct all tests that specify the Heating
Minimum Air Volume Rate--(i.e., the H01, H11,
H21, and H31 Tests)--at an external static
pressure that does not cause an automatic shutdown of the indoor
blower while being as close to, but not less thanor air volume rate
variation QVar, defined in section 3.1.4.1.1.b, greater
than 10 percent, while being as close to, but not less than the
target minimum external static pressure. Additional test steps as
described in section 3.9.1(c) of this appendix are required if the
measured external static pressure exceeds the target value by more
than 0.03 inches of water.
c. For ducted two-capacity northern heat pumps that are tested
with an indoor blower installed, use the appropriate approach of the
above two cases.
d. For ducted two-capacity heat pumps that are tested without an
indoor blower installed, use the Cooling Minimum Air Volume Rate as
the Heating Minimum Air Volume Rate. For ducted two-capacity
northern heat pumps that are tested without an indoor blower
installed, use the Cooling Full-load Air Volume Rate as the Heating
Minimum Air Volume Rate. For ducted two-capacity heating-only heat
pumps that are tested without an indoor blower installed, the
Heating Minimum Air Volume Rate is the higher of the rate specified
by the manufacturer in the test setup instructions included with the
unit or 75 percent of the Heating Full-load Air Volume Rate. During
the laboratory tests on a coil-only system, obtain the Heating
Minimum Air Volume Rate without regard to the pressure drop across
the indoor coil assembly.
e. For non-ducted heat pumps, the Heating Minimum Air Volume
Rate is the air volume rate that results during each test when the
unit operates at an external static pressure of zero inches of water
and at the indoor blower setting used at low compressor capacity
(two-capacity system) or minimum compressor speed (variable-speed
system). For units having a single-speed compressor and a variable-
speed, variable-air-volume-rate indoor blower, use the lowest fan
setting allowed for heating.
f. For ducted systems with multiple indoor blowers within a
single indoor section, obtain the heating minimum air volume rate
using the same ``on'' blowers as used for the cooling minimum air
volume rate. For systems where individual blowers regulate the speed
(as opposed to the cfm) of the indoor blower, use the first section
3.1.4.5 equation for each blower individually. Sum the individual
blower air volume rates to obtain the heating minimum air volume
rate for the system.
3.1.4.6 Heating Intermediate Air Volume Rate.
The manufacturer must specify the heating intermediate air
volume rate and the
[[Page 69413]]
instructions for setting fan speed or controls. Calculate target
minimum external static pressure as described in section 3.1.4.2.
a. For ducted heat pumps tested with an indoor blower installed
that is not a constant-air-volume indoor blower, adjust for external
static pressure as described in section 3.1.4.2.a for cooling
minimum air volume rate.
b. For ducted heat pumps tested with constant-air-volume indoor
blowers installed, conduct the H2V Test at an external
static pressure that does not cause an automatic shutdown of the
indoor blower or air volume rate variation QVar, defined
in section 3.1.4.1.1.b, greater than 10 percent, while being as
close to, but not less than the target minimum external static
pressure. Additional test steps as described in section 3.9.1(c) of
this appendix are required if the measured external static pressure
exceeds the target value by more than 0.03 inches of water.
c. For non-ducted heat pumps, the Heating Intermediate Air
Volume Rate is the air volume rate that results when the heat pump
operates at an external static pressure of zero inches of water and
at the fan speed selected by the controls of the unit for the
H2V Test conditions.
3.1.4.7 Heating Nominal Air Volume Rate.
The manufacturer must specify the heating nominal air volume
rate and the instructions for setting fan speed or controls.
Calculate target minimum external static pressure as described in
section 3.1.4.2. Make adjustments as described in section 3.14.6 for
heating intermediate air volume rate so that the target minimum
external static pressure is met or exceeded.
3.1.5 Indoor test room requirement when the air surrounding the
indoor unit is not supplied from the same source as the air entering
the indoor unit.
If using a test set-up where air is ducted directly from the air
reconditioning apparatus to the indoor coil inlet (see Figure 2,
Loop Air-Enthalpy Test Method Arrangement, of ASHRAE Standard 37-
2009), maintain the dry bulb temperature within the test room within
5.0 [deg]F of the applicable sections 3.2 and 3.6 dry
bulb temperature test condition for the air entering the indoor
unit. Dew point shall be within 2 [deg]F of the required inlet
conditions.
3.1.6 Air volume rate calculations.
For all steady-state tests and for Frost Accumulation (H2,
H21, H22, H2V) tests, calculate the
air volume rate through the indoor coil as specified in sections
7.7.2.1 and 7.7.2.2 of ASHRAE Standard 37-2009. When using the
Outdoor Air Enthalpy Method, follow sections 7.7.2.1 and 7.7.2.2 to
calculate the air volume rate through the outdoor coil. To express
air volume rates in terms of standard air, use:
[GRAPHIC] [TIFF OMITTED] TP09NO15.222
where,
Vis = air volume rate of standard (dry) air, (ft\3\/
min)da
Vimx = air volume rate of the air-water vapor mixture,
(ft\3\/min)mx
vn' = specific volume of air-water vapor mixture at the
nozzle, ft\3\ per lbm of the air-water vapor mixture
Wn = humidity ratio at the nozzle, lbm of water vapor per
lbm of dry air
0.075 = the density associated with standard (dry) air, (lbm/ft\3\)
vn = specific volume of the dry air portion of the
mixture evaluated at the dry-bulb temperature, vapor content, and
barometric pressure existing at the nozzle, ft\3\ per lbm of dry
air.
[GRAPHIC] [TIFF OMITTED] TP09NO15.223
3.1.7 Test sequence.
Manufacturers may optionally operate the equipment under test
for a ``break-in'' period, not to exceed 20 hours, prior to
conducting the test method specified in this section. A manufacturer
who elects to use this optional compressor break-in period in its
certification testing should record this information (including the
duration) in the test data underlying the certified ratings that are
required to be maintained under 10 CFR 429.71. When testing a ducted
unit (except if a heating-only heat pump), conduct the A or
A2 Test first to establish the Cooling Full-load Air
Volume Rate. For ducted heat pumps where the Heating and Cooling
Full-load Air Volume Rates are different, make the first heating
mode test one that requires the Heating Full-load Air Volume Rate.
For ducted heating-only heat pumps, conduct the H1 or H12
Test first to establish the Heating Full-load Air Volume Rate. When
conducting an cyclic test, always conduct it immediately after the
steady-state test that requires the same test conditions. For
variable-speed systems, the first test using the Cooling Minimum Air
Volume Rate should precede the EV Test, and the first
test using the Heating Minimum Air Volume Rate must precede the
H2V Test. The test laboratory makes all other decisions
on the test sequence.
3.1.8 Requirement for the air temperature distribution leaving
the indoor coil.
For at least the first cooling mode test and the first heating
mode test, monitor the temperature distribution of the air leaving
the indoor coil using the grid of individual sensors described in
sections 2.5 and 2.5.4. For the 30-minute data collection interval
used to determine capacity, the maximum spread among the outlet dry
bulb temperatures from any data sampling must not exceed 1.5 [deg]F.
Install the mixing devices described in section 2.5.4.2 to minimize
the temperature spread.
3.1.9 Requirement for the air temperature distribution entering
the outdoor coil.
Monitor the temperatures of the air entering the outdoor coil
using the grid of temperature sensors described in section 2.11. For
the 30-minute data collection interval used to determine capacity,
the maximum difference between dry bulb temperatures measured at any
of these locations must not exceed 1.5 [deg]F.
3.1.10 Control of auxiliary resistive heating elements.
Except as noted, disable heat pump resistance elements used for
heating indoor air at all times, including during defrost cycles and
if they are normally regulated by a heat comfort controller. For
heat pumps equipped with a heat comfort controller, enable the heat
pump resistance elements only during the below-described, short
test. For single-speed heat pumps covered under section 3.6.1, the
short test follows the H1 or, if conducted, the H1C Test. For two-
capacity heat pumps and heat pumps covered under section 3.6.2, the
short test follows the H12 Test. Set the heat comfort
controller to provide the maximum supply air temperature. With the
heat pump operating and while maintaining the Heating Full-load Air
Volume Rate, measure the temperature of the air leaving the indoor-
side beginning 5 minutes after activating the heat comfort
controller. Sample the outlet dry-bulb temperature at regular
intervals that span 5 minutes or less. Collect data for 10 minutes,
obtaining at least 3 samples. Calculate the average outlet
temperature over the 10-minute interval, TCC.
[[Page 69414]]
3.2 Cooling mode tests for different types of air conditioners
and heat pumps.
3.2.1 Tests for a unit having a single-speed compressor, or a
system comprised of independently circuited single-speed
compressors, that is tested with a fixed-speed indoor blower
installed, with a constant-air-volume-rate indoor blower installed,
or with no indoor blower installed.
Conduct two steady-state wet coil tests, the A and B Tests. Use
the two dry-coil tests, the steady-state C Test and the cyclic D
Test, to determine the cooling mode cyclic degradation coefficient,
CD\c\. If testing outdoor units of central air
conditioners or heat pumps that are not sold with indoor units,
assign CD\c\ the default value of 0.2. Table 4 specifies
test conditions for these four tests.
Table 4--Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor
Blower, a Constant Air Volume Rate Indoor Blower, or No Indoor Blower
----------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F) Cooling air
Test description ---------------------------------------------------------------- volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
----------------------------------------------------------------------------------------------------------------
A Test--required (steady, wet 80 67 95 \1\ 75 Cooling full-
coil). load.\2\
B Test--required (steady, wet 80 67 82 \1\ 65 Cooling full-
coil). load.\2\
C Test--required (steady, dry 80 (\3\) 82 .............. Cooling full-
coil). load.\2\
D Test--required (cyclic, dry 80 (\3\) 82 .............. (\4\).
coil).
----------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is
recommended that an indoor wet-bulb temperature of 57 [deg]F or less be used.)
\4\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the
same pressure difference or velocity pressure as measured during the C Test.
3.2.2 Tests for a unit having a single-speed compressor where
the indoor section uses a single variable-speed variable-air-volume
rate indoor blower or multiple blowers.
3.2.2.1 Indoor blower capacity modulation that correlates with
the outdoor dry bulb temperature or systems with a single indoor
coil but multiple blowers.
Conduct four steady-state wet coil tests: The A2,
A1, B2, and B1 Tests. Use the two
dry-coil tests, the steady-state C1 Test and the cyclic
D1 Test, to determine the cooling mode cyclic degradation
coefficient, Cc.
3.2.2.2 Indoor blower capacity modulation based on adjusting the
sensible to total (S/T) cooling capacity ratio.
The testing requirements are the same as specified in section
3.2.1 and Table 4. Use a Cooling Full-load Air Volume Rate that
represents a normal installation. If performed, conduct the steady-
state C Test and the cyclic D Test with the unit operating in the
same S/T capacity control mode as used for the B Test.
Table 5--Cooling Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.2.2.1 Indoor Unit Requirements
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature ([deg]F) temperature ([deg]F)
Test description ---------------------------------------------------------------- Cooling air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet coil).. 80 67 95 \1\ 75 Cooling full-load.\2\
A1 Test--required (steady, wet coil).. 80 67 95 \1\ 75 Cooling minimum.\3\
B2 Test--required (steady, wet coil).. 80 67 82 \1\65 Cooling full-load.\2\
B1 Test--required (steady, wet coil).. 80 67 82 \1\65 Cooling minimum.\3\
C1 Test\4\--required (steady, dry 80 (\4\) 82 .............. Cooling minimum.\3\
coil).
D1 Test\4\--required (cyclic, dry 80 (\4\) 82 (\5\) ................................................
coil).
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ Defined in section 3.1.4.2.
\4\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb
temperature of 57 [deg]F or less be used.)
\5\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the C1 Test.
3.2.3 Tests for a unit having a two-capacity compressor. (see
section 1.2, Definitions)
a. Conduct four steady-state wet coil tests: The A2,
B2, B1, and F1 Tests. Use the two
dry-coil tests, the steady-state C1 Test and the cyclic
D1 Test, to determine the cooling-mode cyclic-degradation
coefficient, Cc. Table 6 specifies test conditions for these six
tests.
b. For units having a variable speed indoor blower that is
modulated to adjust the sensible to total (S/T) cooling capacity
ratio, use Cooling Full-load and Cooling Minimum Air Volume Rates
that represent a normal installation. Additionally, if conducting
the dry-coil tests, operate the unit in the same S/T capacity
control mode as used for the B1 Test.
c. Test two-capacity, northern heat pumps (see section 1.2,
Definitions) in the same way as a single speed heat pump with the
unit operating exclusively at low compressor capacity (see section
3.2.1 and Table 4).
d. If a two-capacity air conditioner or heat pump locks out low-
capacity operation at higher outdoor temperatures, then use the two
dry-coil tests, the steady-state C2 Test and the cyclic
D2 Test, to determine the cooling-mode cyclic-degradation
coefficient that only applies to on/off cycling from high capacity,
Cc(k=2). The default CO\c\(k=2) is the same value as
determined or assigned for the low-capacity cyclic-degradation
coefficient, Cc [or equivalently, Cc(k=1)].
[[Page 69415]]
Table 6--Cooling Mode Test Conditions for Units Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor
temperature ([deg]F) unit temperature
Test description -------------------------- ([deg]F) Compressor capacity Cooling air volume rate
--------------------------
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet coil)..... 80 67 95 \1\ 75 High........................ Cooling Full-Load.\2\
B2 Test--required (steady, wet coil)..... 80 67 82 \1\ 65 High........................ Cooling Full-Load.\2\
B1 Test--required (steady, wet coil)..... 80 67 82 \1\ 65 Low......................... Cooling Minimum.\3\
C2 Test--required (steady, dry-coil)..... 80 (\4\) 82 High Cooling Full-Load.\2\....... ...........................
D2 Test--required (cyclic, dry-coil)..... 80 (\4\) 82 High (\5\)....................... ...........................
C1 Test--required (steady, dry-coil)..... 80 (\4\) 82 Low Cooling Minimum.\3\......... ...........................
D1 Test--required (cyclic, dry-coil)..... 80 (\4\) 82 Low (\6\)....................... ...........................
F1 Test--required (steady, wet coil)..... 80 67 67 \1\ 53.5 Low......................... Cooling Minimum.\3\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ Defined in section 3.1.4.2.
\4\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet-bulb
temperature of 57 [deg]F or less.
\5\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the C2 Test.
\6\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the C1 Test.
3.2.4 Tests for a unit having a variable-speed compressor.
a. Conduct five steady-state wet coil tests: The A2,
EV, B2, B1, and F1
Tests. Use the two dry-coil tests, the steady-state G1
Test and the cyclic I1 Test, to determine the cooling
mode cyclic degradation coefficient, CD\c\..-Table-7
specifies test conditions for these seven tests. Determine the
intermediate compressor speed cited in Table 7 using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.224
where a tolerance of plus 5 percent or the next higher inverter
frequency step from that calculated is allowed.
b. For units that modulate the indoor blower speed to adjust the
sensible to total (S/T) cooling capacity ratio, use Cooling Full-
load, Cooling Intermediate, and Cooling Minimum Air Volume Rates
that represent a normal installation. Additionally, if conducting
the dry-coil tests, operate the unit in the same S/T capacity
control mode as used for the F1 Test.
c. For multiple-split air conditioners and heat pumps (except
where noted), the following procedures supersede the above
requirements: For all Table 7 tests specified for a minimum
compressor speed, at least one indoor unit must be turned off. The
manufacturer shall designate the particular indoor unit(s) that is
turned off. The manufacturer must also specify the compressor speed
used for the Table 7 EV Test, a cooling-mode intermediate
compressor speed that falls within \1/4\ and \3/4\ of the difference
between the maximum and minimum cooling-mode speeds. The
manufacturer should prescribe an intermediate speed that is expected
to yield the highest EER for the given EV Test conditions
and bracketed compressor speed range. The manufacturer can designate
that one or more indoor units are turned off for the EV
Test.
Table 7--Cooling Mode Test Condition for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor
temperature ([deg]F) unit temperature
Test description -------------------------- ([deg]F) Compressor speed Cooling air volume rate
--------------------------
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
A2 Test--required (steady, wet coil)..... 80 67 95 \1\ 75 Maximum..................... Cooling Full-Load.\2\
B2 Test--required (steady, wet coil)..... 80 67 82 \1\ 65 Maximum..................... Cooling Full-Load.\2\
EV Test--required (steady, wet coil)..... 80 67 87 \1\ 69 Intermediate................ Cooling Intermediate.\3\
B1 Test--required (steady, wet coil)..... 80 67 82 \1\ 65 Minimum..................... Cooling Minimum.\4\
F1 Test--required (steady, wet coil)..... 80 67 67 \1\ 53.5 Minimum..................... Cooling Minimum.\4\
G1 Test \5\--required (steady, dry-coil). 80 (\6\) 67 Minimum Cooling Minimum.\4\.........
I1 Test \5\--required (cyclic, dry-coil). 80 (\6\) 67 Minimum (\6\).......................
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ The specified test condition only applies if the unit rejects condensate to the outdoor coil.
\2\ Defined in section 3.1.4.1.
\3\ Defined in section 3.1.4.3.
\4\ Defined in section 3.1.4.2.
\5\ The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet bulb
temperature of 57 [deg]F or less.
\6\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity
pressure as measured during the G1 Test.
3.2.5 Cooling mode tests for northern heat pumps with triple-
capacity compressors.
Test triple-capacity, northern heat pumps for the cooling mode
in the same way as specified in section 3.2.3 for units having a
two-capacity compressor.
[[Page 69416]]
3.2.6 Tests for an air conditioner or heat pump having a single
indoor unit having multiple blowers and offering two stages of
compressor modulation.
Conduct the cooling mode tests specified in section 3.2.3.
3.3 Test procedures for steady-state wet coil cooling mode tests
(the A, A2, A1, B, B2,
B1, EV, and F1 Tests).
a. For the pretest interval, operate the test room
reconditioning apparatus and the unit to be tested until maintaining
equilibrium conditions for at least 30 minutes at the specified
section 3.2 test conditions. Use the exhaust fan of the airflow
measuring apparatus and, if installed, the indoor blower of the test
unit to obtain and then maintain the indoor air volume rate and/or
external static pressure specified for the particular test.
Continuously record (see section 1.2, Definitions):
(1) The dry-bulb temperature of the air entering the indoor
coil,
(2) The water vapor content of the air entering the indoor coil,
(3) The dry-bulb temperature of the air entering the outdoor
coil, and
(4) For the section 2.2.4 cases where its control is required,
the water vapor content of the air entering the outdoor coil.
Refer to section 3.11 for additional requirements that depend on
the selected secondary test method.
b. After satisfying the pretest equilibrium requirements, make
the measurements specified in Table 3 of ASHRAE Standard 37-2009
(incorporated by reference, see Sec. 430.3) for the Indoor Air
Enthalpy method and the user-selected secondary method. Make said
Table 3 measurements at equal intervals that span 5 minutes or less.
Continue data sampling until reaching a 30-minute period (e.g., four
consecutive 10-minute samples) where the test tolerances specified
in Table 8 are satisfied. For those continuously recorded
parameters, use the entire data set from the 30-minute interval to
evaluate Table 8 compliance. Determine the average electrical power
consumption of the air conditioner or heat pump over the same 30-
minute interval.
c. Calculate indoor-side total cooling capacity and sensible
cooling capacity as specified in sections 7.3.3.1 and 7.3.3.3 of
ASHRAE Standard 37-2009. Do not adjust the parameters used in
calculating capacity for the permitted variations in test
conditions. Evaluate air enthalpies based on the measured barometric
pressure. Use the values of the specific heat of air given in
section 7.3.3.1 for calculation of the sensible cooling capacities.
Assign the average total space cooling capacity, average sensible
cooling capacity, and electrical power consumption over the 30-
minute data collection interval to the variables Qck(T), Qsck(T) and
[Edot]ck(T), respectively. For these three variables, replace the
``T'' with the nominal outdoor temperature at which the test was
conducted. The superscript k is used only when testing multi-
capacity units. Use the superscript k=2 to denote a test with the
unit operating at high capacity or maximum speed, k=1 to denote low
capacity or minimum speed, and k=v to denote the intermediate speed.
d. For units tested without an indoor blower installed, decrease
Qc\k\(T) by
[GRAPHIC] [TIFF OMITTED] TP09NO15.225
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
Table 8--Test Operating and Test Condition Tolerances for Section 3.3
Steady-State Wet Coil Cooling Mode Tests and Section 3.4 Dry Coil
Cooling Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor dry-bulb, [deg]F:
Entering temperature................ 2.0 0.5
Leaving temperature................. 2.0
Indoor wet-bulb, [deg]F:
Entering temperature................ 1.0 \2\ 0.3
Leaving temperature................. \2\ 1.0
Outdoor dry-bulb, [deg]F:
Entering temperature................ 2.0 0.5
Leaving temperature................. \3\ 2.0
Outdoor wet-bulb, [deg]F:
Entering temperature................ 1.0 \4\ 0.3
Leaving temperature................. \3\ 1.0
External resistance to airflow, inches 0.12 \5\ 0.02
of water...............................
Electrical voltage, % of rdg............ 2.0 1.5
Nozzle pressure drop, % of rdg.......... 8.0
------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Only applies during wet coil tests; does not apply during steady-
state, dry coil cooling mode tests.
\3\ Only applies when using the Outdoor Air Enthalpy Method.
\4\ Only applies during wet coil cooling mode tests where the unit
rejects condensate to the outdoor coil.
\5\ Only applies when testing non-ducted units.
e. For air conditioners and heat pumps having a constant-air-
volume-rate indoor blower, the five additional steps listed below
are required if the average of the measured external static
pressures exceeds the applicable sections 3.1.4 minimum (or target)
external static pressure ([Delta]Pmin) by 0.03 inches of
water or more.
1. Measure the average power consumption of the indoor blower
motor (Efan,1) and record the corresponding external
static pressure ([Delta]P1) during or immediately
following the 30-
[[Page 69417]]
minute interval used for determining capacity.
2. After completing the 30-minute interval and while maintaining
the same test conditions, adjust the exhaust fan of the airflow
measuring apparatus until the external static pressure increases to
approximately [Delta]P1 + ([Delta]P1 -
[Delta]Pmin).
3. After re-establishing steady readings of the fan motor power
and external static pressure, determine average values for the
indoor blower power (Efan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
4. Approximate the average power consumption of the indoor
blower motor at [Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TP09NO15.226
5. Increase the total space cooling capacity,
Qc\k\(T), by the quantity (Efan,1 -
Efan,min), when expressed on a Btu/h basis. Decrease the
total electrical power, Ec\k\(T), by the same fan power
difference, now expressed in watts.
3.4 Test procedures for the steady-state dry-coil cooling-mode
tests (the C, C1, C2, and G1
Tests).
a. Except for the modifications noted in this section, conduct
the steady-state dry coil cooling mode tests as specified in section
3.3 for wet coil tests. Prior to recording data during the steady-
state dry coil test, operate the unit at least one hour after
achieving dry coil conditions. Drain the drain pan and plug the
drain opening. Thereafter, the drain pan should remain completely
dry.
b. Denote the resulting total space cooling capacity and
electrical power derived from the test as Qss,dry and
Ess,dry. With regard to a section 3.3 deviation, do not
adjust Qss,dry for duct losses (i.e., do not apply
section 7.3.3.3 of ASHRAE Standard 37-2009). In preparing for the
section 3.5 cyclic tests, record the average indoor-side air volume
rate, Vi, specific heat of the air, Cp,a (expressed on dry air
basis), specific volume of the air at the nozzles, v'n,
humidity ratio at the nozzles, Wn, and either pressure
difference or velocity pressure for the flow nozzles. For units
having a variable-speed indoor fan (that provides either a constant
or variable air volume rate) that will or may be tested during the
cyclic dry coil cooling mode test with the indoor fan turned off
(see section 3.5), include the electrical power used by the indoor
fan motor among the recorded parameters from the 30-minute test.
c. If the temperature sensors used to provide the primary
measurement of the indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the subsequent cyclic dry-
coil test are different, include measurements of the latter sensors
among the regularly sampled data. Beginning at the start of the 30-
minute data collection period, measure and compute the indoor-side
air dry-bulb temperature difference using both sets of
instrumentation, [Delta]T (Set SS) and [Delta]T (Set CYC), for each
equally spaced data sample. If using a consistent data sampling rate
that is less than 1 minute, calculate and record minutely averages
for the two temperature differences. If using a consistent sampling
rate of one minute or more, calculate and record the two temperature
differences from each data sample. After having recorded the seventh
(i=7) set of temperature differences, calculate the following ratio
using the first seven sets of values:
[GRAPHIC] [TIFF OMITTED] TP09NO15.227
Each time a subsequent set of temperature differences is
recorded (if sampling more frequently than every 5 minutes),
calculate FCD using the most recent seven sets of values.
Continue these calculations until the 30-minute period is completed
or until a value for FCD is calculated that falls outside
the allowable range of 0.94-1.06. If the latter occurs, immediately
suspend the test and identify the cause for the disparity in the two
temperature difference measurements. Recalibration of one or both
sets of instrumentation may be required. If all the values for
FCD are within the allowable range, save the final value
of the ratio from the 30-minute test as FCD*. If the
temperature sensors used to provide the primary measurement of the
indoor-side dry bulb temperature difference during the steady-state
dry- coil test and the subsequent cyclic dry-coil test are the same,
set FCD*= 1.
3.5 Test procedures for the cyclic dry-coil cooling-mode tests
(the D, D1, D2, and I1 Tests).
a. After completing the steady-state dry-coil test, remove the
Outdoor Air Enthalpy method test apparatus, if connected, and begin
manual OFF/ON cycling of the unit's compressor. The test set-up
should otherwise be identical to the set-up used during the steady-
state dry coil test. When testing heat pumps, leave the reversing
valve during the compressor OFF cycles in the same position as used
for the compressor ON cycles, unless automatically changed by the
controls of the unit. For units having a variable-speed indoor
blower, the manufacturer has the option of electing at the outset
whether to conduct the cyclic test with the indoor blower enabled or
disabled. Always revert to testing with the indoor blower disabled
if cyclic testing with the fan enabled is unsuccessful.
b. For units having a single-speed or two-capacity compressor,
cycle the compressor OFF for 24 minutes and then ON for 6 minutes
([Delta][tau]cyc,dry = 0.5 hours). For units having a
variable-speed compressor, cycle the compressor OFF for 48 minutes
and then ON for 12 minutes ([Delta][tau]cyc,dry = 1.0
hours). Repeat the OFF/ON compressor cycling pattern until the test
is completed. Allow the controls of the unit to regulate cycling of
the outdoor fan. If an upturned duct is used, measure the dry-bulb
temperature at the inlet of the device at least once every minute
and ensure that its test operating tolerance is within 1.0 [deg]F
for each compressor OFF period.
c. Sections 3.5.1 and 3.5.2 specify airflow requirements through
the indoor coil of ducted and non-ducted systems, respectively. In
all cases, use the exhaust fan of the airflow measuring apparatus
(covered under section 2.6) along with the indoor blower of the
unit, if installed and operating, to approximate a step response in
the indoor coil airflow. Regulate the exhaust fan to quickly obtain
and then maintain the flow nozzle static pressure difference or
velocity pressure at the same value as was measured during the
steady-state dry coil test. The pressure difference or velocity
pressure should be within 2 percent of the value from the steady-
state dry coil test within 15 seconds after airflow initiation. For
units having a variable-speed indoor blower that ramps when cycling
on and/or off, use the exhaust fan of the airflow measuring
apparatus to impose a step response that begins at the initiation of
ramp up and ends at the termination of ramp down.
d. For units having a variable-speed indoor blower, conduct the
cyclic dry coil test using the pull-thru approach described below if
any of the following occur when testing with the fan operating:
(1) The test unit automatically cycles off;
(2) Its blower motor reverses; or
[[Page 69418]]
(3) The unit operates for more than 30 seconds at an external
static pressure that is 0.1 inches of water or more higher than the
value measured during the prior steady-state test.
For the pull-thru approach, disable the indoor blower and use
the exhaust fan of the airflow measuring apparatus to generate the
specified flow nozzles static pressure difference or velocity
pressure. If the exhaust fan cannot deliver the required pressure
difference because of resistance created by the unpowered blower,
temporarily remove the blower.
e. Conduct a minimum of six complete compressor OFF/ON cycles
for a unit with a single-speed or two-speed compressor, and a
minimum of five complete compressor OFF/ON cycles for a unit with a
variable speed compressor. The first three cycles for a unit with a
single-speed compressor or two-speed compressor and the first two
cycles for a unit with a unit with a variable speed compressor are
the warm-up period--the later cycles are called the active cycles.
Calculate the degradation coefficient CD for each
complete active cycle if the test tolerances given in Table 9 are
satisfied. If the average CD for the first three active
cycles is within 0.02 of the average CD for the first two
active cycles, use the average CD of the three active
cycles as the final result. If these averages differ by more than
0.02, continue the test to get CD for the fourth cycle.
If the average CD of the last three cycles is lower than
or no more than 0.02 greater than the average CD of the
first three cycles, use the average CD of all four active
cycles as the final result. Otherwise, continue the test with a
fifth cycle. If the average CD of the last three cycles
is 0.02 higher than the average for the previous three cycles, use
the default CD, otherwise use the average CD
of all five active cycles. If the test tolerances given in Table 9
are not satisfied, use default CD value. The default
CD value for cooling is 0.2.
f. With regard to the Table 9 parameters, continuously record
the dry-bulb temperature of the air entering the indoor and outdoor
coils during periods when air flows through the respective coils.
Sample the water vapor content of the indoor coil inlet air at least
every 2 minutes during periods when air flows through the coil.
Record external static pressure and the air volume rate indicator
(either nozzle pressure difference or velocity pressure) at least
every minute during the interval that air flows through the indoor
coil. (These regular measurements of the airflow rate indicator are
in addition to the required measurement at 15 seconds after flow
initiation.) Sample the electrical voltage at least every 2 minutes
beginning 30 seconds after compressor start-up. Continue until the
compressor, the outdoor fan, and the indoor blower (if it is
installed and operating) cycle off.
g. For ducted units, continuously record the dry-bulb
temperature of the air entering (as noted above) and leaving the
indoor coil. Or if using a thermopile, continuously record the
difference between these two temperatures during the interval that
air flows through the indoor coil. For non-ducted units, make the
same dry-bulb temperature measurements beginning when the compressor
cycles on and ending when indoor coil airflow ceases.
h. Integrate the electrical power over complete cycles of length
[Delta][tau]cyc,dry. For ducted units tested with an
indoor blower installed and operating, integrate electrical power
from indoor blower OFF to indoor blower OFF. For all other ducted
units and for non-ducted units, integrate electrical power from
compressor OFF to compressor OFF. (Some cyclic tests will use the
same data collection intervals to determine the electrical energy
and the total space cooling. For other units, terminate data
collection used to determine the electrical energy before
terminating data collection used to determine total space cooling.)
Table 9--Test Operating and Test Condition Tolerances for Cyclic Dry
Coil Cooling Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor entering dry-bulb temperature,\2\ 2.0 0.5
[deg]F.................................
Indoor entering wet-bulb temperature, .............. (\3\)
[deg]F.................................
Outdoor entering dry-bulb 2.0 0.5
temperature,\2\ [deg]F.................
External resistance to airflow,\2\ 0.12 ..............
inches of water........................
Airflow nozzle pressure difference or 8.0 \4\ 2.0
velocity pressure,\2\ % of reading.....
Electrical voltage,\5\% of rdg.......... 2.0 1.5
------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Applies during the interval that air flows through the indoor
(outdoor) coil except for the first 30 seconds after flow initiation.
For units having a variable-speed indoor blower that ramps, the
tolerances listed for the external resistance to airflow apply from 30
seconds after achieving full speed until ramp down begins.
\3\ Shall at no time exceed a wet-bulb temperature that results in
condensate forming on the indoor coil.
\4\ The test condition shall be the average nozzle pressure difference
or velocity pressure measured during the steady-state dry coil test.
\5\ Applies during the interval when at least one of the following--the
compressor, the outdoor fan, or, if applicable, the indoor blower--are
operating except for the first 30 seconds after compressor start-up.
i. If the Table 9 tolerances are satisfied over the complete
cycle, record the measured electrical energy consumption as
ecyc,dry and express it in units of watt-hours. Calculate
the total space cooling delivered, qcyc,dry, in units of
Btu using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.228
where Vi, Cp,a, vn' (or vn),
Wn, and FCD* are the values recorded during
the section 3.4 dry coil steady-state test and
Tal([tau]) = dry bulb temperature of the air entering the
indoor coil at time [tau], [deg]F.
Ta2([tau]) = dry bulb temperature of the air leaving the
indoor coil at time [tau], [deg]F.
[tau]1 = for ducted units, the elapsed time when airflow
is initiated through the indoor coil; for non-ducted units, the
elapsed time when the compressor is cycled on, hr.
[tau]2 = the elapsed time when indoor coil airflow
ceases, hr.
3.5.1 Procedures when testing ducted systems.
The automatic controls that are normally installed with the test
unit must govern the OFF/ON cycling of the air moving equipment on
the indoor side (exhaust fan of the airflow measuring apparatus and,
if installed, the indoor blower of the test unit). For example, for
ducted units tested without an indoor blower installed but rated
based on using a fan time delay relay, control the indoor coil
airflow according to the rated ON and/or OFF delays provided by the
relay. For ducted units having a variable-speed indoor blower that
has been disabled (and possibly removed), start and stop the indoor
airflow at the same instances as if the fan were enabled. For all
other ducted units tested without an indoor blower installed, cycle
the indoor coil airflow in unison with the cycling of the
compressor. If air damper boxes are used, close them on the inlet
and outlet side during the OFF period. Airflow through the indoor
coil should stop within 3 seconds
[[Page 69419]]
after the automatic controls of the test unit (act to) de-energize
the indoor blower. For ducted units tested without an indoor blower
installed (excluding the special case where a variable-speed fan is
temporarily removed), increase ecyc,dry by the quantity,
Equation 3.5-2 (441W/1000scfm) * Vi * [[tau]2-
[tau]1]
and decrease qcyc,dry by,
Equation 3.5-3 (1505 Btu/h/1000scfm) * Vi * [[tau]2-
[tau]1]
where Vis is the average indoor air volume rate from the
section 3.4 dry coil steady-state test and is expressed in units of
cubic feet per minute of standard air (scfm). For units having a
variable-speed indoor blower that is disabled during the cyclic
test, increase ecyc,dry and decrease qcyc,dry
based on:
a. The product of [[tau]2-[tau]1] and the
indoor blower power measured during or following the dry coil
steady-state test; or,
b. The following algorithm if the indoor blower ramps its speed
when cycling.
1. Measure the electrical power consumed by the variable-speed
indoor blower at a minimum of three operating conditions: At the
speed/air volume rate/external static pressure that was measured
during the steady-state test, at operating conditions associated
with the midpoint of the ramp-up interval, and at conditions
associated with the midpoint of the ramp-down interval. For these
measurements, the tolerances on the airflow volume or the external
static pressure are the same as required for the section 3.4 steady-
state test.
2. For each case, determine the fan power from measurements made
over a minimum of 5 minutes.
3. Approximate the electrical energy consumption of the indoor
blower if it had operated during the cyclic test using all three
power measurements. Assume a linear profile during the ramp
intervals. The manufacturer must provide the durations of the ramp-
up and ramp-down intervals. If the test setup instructions included
with the unit by the manufacturer specifies a ramp interval that
exceeds 45 seconds, use a 45-second ramp interval nonetheless when
estimating the fan energy.
3.5.2 Procedures when testing non-ducted systems.
Do not use airflow prevention devices when conducting cyclic
tests on non-ducted units. Until the last OFF/ON compressor cycle,
airflow through the indoor coil must cycle off and on in unison with
the compressor. For the last OFF/ON compressor cycle--the one used
to determine ecyc,dry and qcyc,dry--use the
exhaust fan of the airflow measuring apparatus and the indoor blower
of the test unit to have indoor airflow start 3 minutes prior to
compressor cut-on and end three minutes after compressor cutoff.
Subtract the electrical energy used by the indoor blower during the
3 minutes prior to compressor cut-on from the integrated electrical
energy, ecyc,dry. Add the electrical energy used by the
indoor blower during the 3 minutes after compressor cutoff to the
integrated cooling capacity, qcyc,dry. For the case where
the non-ducted unit uses a variable-speed indoor blower which is
disabled during the cyclic test, correct ecyc,dry and
qcyc,dry using the same approach as prescribed in section
3.5.1 for ducted units having a disabled variable-speed indoor
blower.
3.5.3 Cooling-mode cyclic-degradation coefficient calculation.
Use the two dry-coil tests to determine the cooling-mode cyclic-
degradation coefficient, CD\c\. Append ``(k=2)'' to the
coefficient if it corresponds to a two-capacity unit cycling at high
capacity. Evaluate CD\c\ using the above results and
those from the section 3.4 dry-coil steady-state test.
[GRAPHIC] [TIFF OMITTED] TP09NO15.230
the average energy efficiency ratio during the cyclic dry coil
cooling mode test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TP09NO15.231
the average energy efficiency ratio during the steady-state dry coil
cooling mode test, Btu/W[middot]h
[GRAPHIC] [TIFF OMITTED] TP09NO15.232
Round the calculated value for CD\c\ to the nearest
0.01. If CD\c\ is negative, then set it equal to zero.
3.6 Heating mode tests for different types of heat pumps,
including heating-only heat pumps.
3.6.1 Tests for a heat pump having a single-speed compressor
that is tested with a fixed speed indoor blower installed, with a
constant-air-volume-rate indoor blower installed, or with no indoor
blower installed.
Conduct the High Temperature Cyclic (H1C) Test to determine the
heating mode cyclic-degradation coefficient, CD\h\. Test
conditions for the four tests are specified in Table 10.
[[Page 69420]]
Table 10--Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor
Blower, a Constant Air Volume Rate Indoor Blower, or No Indoor Blower
----------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor
temperature ([deg]F) unit temperature
Test description -------------------------- ([deg]F) Heating air volume
-------------------------- rate
Dry bulb Wet bulb Dry bulb Wet bulb
----------------------------------------------------------------------------------------------------------------
H1 Test (required, steady).......... 70 60\(max)\ 47 43 Heating Full-load.\1\
H1C Test (required, cyclic)......... 70 60\(max)\ 47 43 (\2\).
H2 Test (required).................. 70 60\(max)\ 35 33 Heating Full-load.\1\
H3 Test (required, steady).......... 70 60\(max)\ 17 15 Heating Full-load.\1\
----------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4.
\2\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the
same pressure difference or velocity pressure as measured during the H1 Test.
3.6.2 Tests for a heat pump having a single-speed compressor and
a single indoor unit having either (1) a variable speed, variable-
air-rate indoor blower whose capacity modulation correlates with
outdoor dry bulb temperature or (2) multiple blowers.
Conduct five tests: Two High Temperature Tests (H12
and H11), one Frost Accumulation Test (H22),
and two Low Temperature Tests (H32 and H31).
Conducting an additional Frost Accumulation Test (H21) is
optional. Conduct the High Temperature Cyclic (H1C1) Test
to determine the heating mode cyclic-degradation coefficient,
CD\h\. Test conditions for the seven tests are specified
in Table 11. If the optional H21 Test is not performed,
use the following equations to approximate the capacity and
electrical power of the heat pump at the H21 test
conditions:
[GRAPHIC] [TIFF OMITTED] TP09NO15.233
[GRAPHIC] [TIFF OMITTED] TP09NO15.234
The quantities Qh\k=2\(47),
[Edot]h\k=2\(47), Qh\k=1\(47), and
[Edot]h\k=1\(47) are determined from the H12
and H11 Tests and evaluated as specified in section 3.7;
the quantities Qh\k=2\(35) and
[Edot]h\k=2\(35) are determined from the H22
Test and evaluated as specified in section 3.9; and the quantities
Qh\k=2\(17), [Edot]h\k=2\(17),
Qh\k=1\(17), and [Edot]h\k=1\(17), are
determined from the H32 and H31 Tests and
evaluated as specified in section 3.10.
Table 11--Heating Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.6.2
Indoor Unit Requirements
----------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor
temperature ([deg]F) unit temperature
Test description -------------------------- ([deg]F) Heating air volume
-------------------------- rate
Dry bulb Wet bulb Dry bulb Wet bulb
----------------------------------------------------------------------------------------------------------------
H12 Test (required, steady)......... 70 60\(max)\ 47 43 Heating Full-load.\1\
H11 Test (required, steady)......... 70 60\(max)\ 47 43 Heating Minimum.\2\
H1C1 Test (required, cyclic)........ 70 60\(max)\ 47 43 (\3\).
H22 Test (required)................. 70 60\(max)\ 35 33 Heating Full-load.\1\
H21 Test (optional)................. 70 60\(max)\ 35 33 Heating Minimum.\2\
H32 Test (required, steady)......... 70 60\(max)\ 17 15 Heating Full-load.\1\
H31 Test (required, steady)......... 70 60\(max)\ 17 15 Heating Minimum.\2\
----------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.4.
\2\ Defined in section 3.1.4.5.
\3\ Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the
same pressure difference or velocity pressure as measured during the H11 Test.
[[Page 69421]]
3.6.3 Tests for a heat pump having a two-capacity compressor
(see section 1.2, Definitions), including two-capacity, northern
heat pumps (see section 1.2, Definitions).
a. Conduct one Maximum Temperature Test (H01), two
High Temperature Tests (H12and H11), one Frost
Accumulation Test (H22), and one Low Temperature Test
(H32). Conduct an additional Frost Accumulation Test
(H21) and Low Temperature Test (H31) if both
of the following conditions exist:
1. Knowledge of the heat pump's capacity and electrical power at
low compressor capacity for outdoor temperatures of 37[emsp14][deg]F
and less is needed to complete the section 4.2.3 seasonal
performance calculations; and
2. The heat pump's controls allow low-capacity operation at
outdoor temperatures of 37[emsp14][deg]F and less.
If the above two conditions are met, an alternative to
conducting the H21 Frost Accumulation is to use the
following equations to approximate the capacity and electrical
power:
[GRAPHIC] [TIFF OMITTED] TP09NO15.235
Determine the quantities Qh\k=1\ (47) and
[Edot]h\k=1\ (47) from the H11 Test and
evaluate them according to Section 3.7. Determine the quantities
Qh\k=1\ (17) and [Edot]h\k=1\ (17) from the
H31 Test and evaluate them according to Section 3.10.
b. Conduct the High Temperature Cyclic Test (H1C1) to
determine the heating mode cyclic-degradation coefficient,
CD\h\. If a two-capacity heat pump locks out low capacity
operation at lower outdoor temperatures, conduct the High
Temperature Cyclic Test (H1C2) to determine the high-
capacity heating mode cyclic-degradation coefficient,
CD\h\ (k=2). Table 12 specifies test conditions for these
nine tests.
Table 12--Heating Mode Test Conditions for Units Having a Two-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor
temperature ([deg]F) unit temperature
Test description -------------------------- ([deg]F) Compressor capacity Heating air volume rate
--------------------------
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).............. 70 60 (max) 62 56.5 Low......................... Heating Minimum.\1\
H12 Test (required, steady).............. 70 60 \(max)\ 47 43 High........................ Heating Full-Load.\2\
H1C2 Test (required,\7\ cyclic).......... 70 60 \(max)\ 47 43 High........................ (\3\)
H11 Test (required)...................... 70 60 \(max)\ 47 43 Low......................... Heating Minimum.\1\
H1C1 Test (required, cyclic)............. 70 60 \(max)\ 47 43 Low......................... (\4\)
H22 Test (required)...................... 70 60 \(max)\ 35 33 High........................ Heating Full-Load.\2\
H21 Test 5 6 (required).................. 70 60 \(max)\ 35 33 Low......................... Heating Minimum.\1\
H32 Test (required, steady).............. 70 60 \(max)\ 17 15 High........................ Heating Full-Load.\2\
H31 Test 5 (required, steady)............ 70 60 \(max)\ 17 15 Low......................... Heating Minimum.\1\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5.
\2\ Defined in section 3.1.4.4.
\3\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H12 Test.
\4\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H11 Test.
\5\ Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 [deg]F is needed to
complete the section 4.2.3 HSPF calculations.
\6\ If table note #5 applies, the section 3.6.3 equations for Qh\k=1\ (35) and [Edot]h\k=1\ (17) may be used in lieu of conducting the H21 Test.
\7\ Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.
3.6.4 Tests for a heat pump having a variable-speed compressor.
a. (1) Conduct one Maximum Temperature Test (H01),
two High Temperature Tests (H12 and H11), one
Frost Accumulation Test (H2V), and one Low Temperature
Test (H32). Conducting one or all of the following tests
is optional: An additional High Temperature Test (H1N),
an additional Frost Accumulation Test (H22), and an
additional Low Temperature Test (H42). Conduct the High
Temperature Cyclic (H1C1) Test to determine the heating
mode cyclic-degradation coefficient, CD\h\. (2) The
optional low ambient temperature test (H42) may be
conducted in place of H12 to allow representation of
heating performance below 17 [deg]F ambient temperature using the
results of H42 and H32 rather than the results
of H32 and H12. This option may not be used
for units which have a cutoff temperature preventing compressor
operation below 12 [deg]F. If H42 is conducted, it is
optional to conduct the H12 test for heating capacity
rating purposes--H1N can be conducted for heating
capacity rating purposes. If H12 is not conducted,
H22 must be conducted.
Test conditions for the nine tests are specified in Table 13.
Determine the intermediate compressor speed cited in Table 13 using
the heating mode maximum and minimum compressors speeds and:
[GRAPHIC] [TIFF OMITTED] TP09NO15.236
Where a tolerance of plus 5 percent or the next higher inverter
frequency step from that calculated is allowed. If the
H22Test is not done, use the following equations to
approximate the capacity and electrical power at the H22
test conditions:
[[Page 69422]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.237
b. Determine the quantities Qh\k=2\(47) and from
[Edot]h\k=2\(47) from the H12 Test and
evaluate them according to section 3.7. Determine the quantities
Qh\k=2\(17) and [Edot]h\k=2\(17) from the
H32 Test and evaluate them according to section 3.10.
Determine the quantities Qh\k=2\(TL) and
[Edot]h\k=2\(TL) from the H42 Test
and evaluate them according to section 3.10. For heat pumps where
the heating mode maximum compressor speed exceeds its cooling mode
maximum compressor speed, conduct the H1N Test if the
manufacturer requests it. If the H1N Test is done,
operate the heat pump's compressor at the same speed as the speed
used for the cooling mode A2 Test.
Table 13--Heating Mode Test Conditions for Units Having a Variable-Speed Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor
temperature ([deg]F) unit temperature
Test description -------------------------- ([deg]F) Compressor speed Heating air volume rate
--------------------------
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).............. 70 60 \(max)\ 62 56.5 Minimum..................... Heating Minimum.\1\
H1C1 Test (required, cyclic)............. 70 60 \(max)\ 47 43 Minimum..................... (\2\).
H12 Test (required, steady).............. 70 60 \(max)\ 47 43 Maximum..................... Heating Full-Load.\3\
H11 Test (required, steady).............. 70 60 \(max)\ 47 43 Minimum..................... Heating Minimum.\1\
H1N Test (optional, steady).............. 70 60 \(max)\ 47 43 Cooling Mode Maximum........ Heating Nominal.\4\
H22 Test (optional)...................... 70 60 \(max)\ 35 33 Maximum..................... Heating Full-Load.\3\
H2V Test (required)...................... 70 60 \(max)\ 35 33 Intermediate................ Heating Intermediate.\5\
H32 Test (required, steady).............. 70 60 \(max)\ 17 15 Maximum..................... Heating Full-Load.\3\
H42 Test (optional, steady) \6\.......... 70 60 \(max)\ \7\ 2 \7\ 1 Maximum \8\................. Heating Full-Load.\3\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5.
\2\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured
during the H01 Test.
\3\ Defined in section 3.1.4.4.
\4\ Defined in section 3.1.4.7.
\5\ Defined in section 3.1.4.6.
\6\ If the maximum speed is limited below 17 [deg]F, this test becomes required.
\7\ If the cutoff temperature is higher than 2 [deg]F, run at the cutoff temperature.
\8\ If maximum speed is limited by unit control, this test should run at the maximum speed allowed by the control, in such case, the speed is different
from the maximum speed defined in the definition section.
c. For multiple-split heat pumps (only), the following
procedures supersede the above requirements. For all Table 13 tests
specified for a minimum compressor speed, at least one indoor unit
must be turned off. The manufacturer shall designate the particular
indoor unit(s) that is turned off. The manufacturer must also
specify the compressor speed used for the Table 13 H2V
Test, a heating mode intermediate compressor speed that falls within
\1/4\ and \3/4\ of the difference between the maximum and minimum
heating mode speeds. The manufacturer should prescribe an
intermediate speed that is expected to yield the highest COP for the
given H2V Test conditions and bracketed compressor speed
range. The manufacturer can designate that one or more specific
indoor units are turned off for the H2V Test.
3.6.5 Additional test for a heat pump having a heat comfort
controller.
Test any heat pump that has a heat comfort controller (see
section 1.2, Definitions) according to section 3.6.1, 3.6.2, or
3.6.3, whichever applies, with the heat comfort controller disabled.
Additionally, conduct the abbreviated test described in section
3.1.9 with the heat comfort controller active to determine the
system's maximum supply air temperature. (Note: Heat pumps having a
variable speed compressor and a heat comfort controller are not
covered in the test procedure at this time.)
3.6.6 Heating mode tests northern heat pumps with triple-
capacity compressors.
Test triple-capacity, northern heat pumps for the heating mode
as follows:
a. Conduct one maximum-temperature test (H01), two
high-temperature tests (H12 and H11), one
Frost Accumulation test (H22), two low-temperature tests
(H32, H33), and one minimum-temperature test
(H43). Conduct an additional Frost Accumulation test
(H21) and low-temperature test (H31) if both
of the following conditions exist: (1) Knowledge of the heat pump's
capacity and electrical power at low compressor capacity for outdoor
temperatures of 37 [deg]F and less is needed to complete the section
4.2.6 seasonal performance calculations; and (2) the heat pump's
controls allow low-capacity operation at outdoor temperatures of 37
[deg]F and less. If the above two conditions are met, an alternative
to conducting the H21 Frost Accumulation Test to
determine Qh\k=1\(35) and [Edot]h\k=1\(35) is
to use the following equations to approximate this capacity and
electrical power:
[GRAPHIC] [TIFF OMITTED] TP09NO15.238
In evaluating the above equations, determine the quantities
Qh\k=1\(47) from the H11 Test and evaluate
them according to section 3.7. Determine the quantities
Qh\k=1\(17) and [Edot]h\k=1\(17) from the
H31 Test and evaluate them according to section 3.10. Use
the
[[Page 69423]]
paired values of Qh\k=1\(35) and Eh\k=1\(35)
derived from conducting the H21 Frost Accumulation Test
and evaluated as specified in section 3.9.1 or use the paired values
calculated using the above default equations, whichever contribute
to a higher Region IV HSPF based on the DHR.
b. Conducting a Frost Accumulation Test (H23) with
the heat pump operating at its booster capacity is optional. If this
optional test is not conducted, determine Qh\k=3\(35) and
[Edot]h\k=3\(35) using the following equations to
approximate this capacity and electrical power:
[GRAPHIC] [TIFF OMITTED] TP09NO15.239
Determine the quantities Qh\k=2\(47) and
[Edot]h\k=2\(47) from the H12 Test and
evaluate them according to section 3.7. Determine the quantities
Qh\k=2\(35) and [Edot]h\k=2\(35) from the
H22Test and evaluate them according to section 3.9.1.
Determine the quantities Qh\k=2\(17) and
[Edot]h\k=2\(17) from the H32Test, determine
the quantities Qh\k=3\(17) and
[Edot]h\k=3\(17) from the H33Test, and
determine the quantities Qh\k=3\(2) and
[Edot]h\k=3\(2) from the H43Test. Evaluate all
six quantities according to section 3.10. Use the paired values of
Qh\k=3\(35) and [Edot]h\k=3\(35) derived from
conducting the H23Frost Accumulation Test and calculated
as specified in section 3.9.1 or use the paired values calculated
using the above default equations, whichever contribute to a higher
Region IV HSPF based on the DHR.
c. Conduct the high-temperature cyclic test (H1C1) to
determine the heating mode cyclic-degradation coefficient,
CD\h\. If a triple-capacity heat pump locks out low
capacity operation at lower outdoor temperatures, conduct the high-
temperature cyclic test (H1C2) to determine the high-
capacity heating mode cyclic-degradation coefficient,
CD\h\ (k=2). The default CD\h\ (k=2) is the
same value as determined or assigned for the low-capacity cyclic-
degradation coefficient, CD\h\ [or equivalently,
CD\h\ (k=1)]. Finally, if a triple-capacity heat pump
locks out both low and high capacity operation at the lowest outdoor
temperatures, conduct the low-temperature cyclic test
(H3C3) to determine the booster-capacity heating mode
cyclic-degradation coefficient, CD\h\ (k=3). The default
CD\h\ (k=3) is the same value as determined or assigned
for the high-capacity cyclic-degradation coefficient,
CD\h\ [or equivalently, CD\h\ (k=2)]. Table 14
specifies test conditions for all 13 tests.
Table 14-- Heating Mode Test Conditions for Units With a Triple-Capacity Compressor
--------------------------------------------------------------------------------------------------------------------------------------------------------
Air entering indoor unit Air entering outdoor unit
temperature [deg]F temperature [deg]F
Test description ----------------------------------------------------------------- Compressor capacity Heating air volume rate
Dry bulb Wet bulb Dry bulb Wet bulb
--------------------------------------------------------------------------------------------------------------------------------------------------------
H01 Test (required, steady).......... 70 60\(max)\ 62 56.5 Low.................... Heating Minimum.\1\
H12 Test (required, steady).......... 70 60 \(max)\ 47 43 High................... Heating Full-Load.\2\
H1C2 Test (required, cyclic)......... 70 60 \(max)\ 47 43 High................... (\3\)
H11 Test (required).................. 70 60 \(max)\ 47 43 Low.................... Heating Minimum.\1\
H1C1 Test (required, cyclic)......... 70 60 \(max)\ 47 43 Low.................... (\4\)
H23 Test (optional, steady).......... 70 60 \(max)\ 35 33 Booster................ Heating Full-Load.\2\
H22 Test (required).................. 70 60 \(max)\ 35 33 High................... Heating Full-Load.\2\
H21 Test (required).................. 70 60 \(max)\ 35 33 Low.................... Heating Minimum.\1\
H33 Test (required, steady).......... 70 60 \(max)\ 17 15 Booster................ Heating Full-Load.\2\
H3C3 Test \(max)\5 6 (required, 70 60 \(max)\ 17 15 Booster................ (\7\)
cyclic).
H32 Test (required, steady).......... 70 60 \(max)\ 17 15 High................... Heating Full-Load.\2\
H31 Test\5\ (required, steady)....... 70 60 \(max)\ 17 15 Low.................... Heating Minimum.\1\
H43 Test (required, steady).......... 70 60 \(max)\ 2 1 Booster................ Heating Full-Load.\2\
--------------------------------------------------------------------------------------------------------------------------------------------------------
\1\ Defined in section 3.1.4.5.
\2\ Defined in section 3.1.4.4.
\3\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H12 Test.
\4\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H11Test.
\5\ Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37[deg]F is needed to
complete the section 4.2.6 HSPF calculations.
[[Page 69424]]
\6\ If table note \5\ applies, the section 3.6.6 equations for Qhk=1(35) and [Edot]hk=1(17) may be used in lieu of conducting the H21 Test.
\7\ Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured
during the H33 Test.
3.7 Test procedures for steady-state Maximum Temperature and
High Temperature heating mode tests (the H01, H1,
H12, H11, and H1N Tests).
a. For the pretest interval, operate the test room
reconditioning apparatus and the heat pump until equilibrium
conditions are maintained for at least 30 minutes at the specified
section 3.6 test conditions. Use the exhaust fan of the airflow
measuring apparatus and, if installed, the indoor blower of the heat
pump to obtain and then maintain the indoor air volume rate and/or
the external static pressure specified for the particular test.
Continuously record the dry-bulb temperature of the air entering the
indoor coil, and the dry-bulb temperature and water vapor content of
the air entering the outdoor coil. Refer to section 3.11 for
additional requirements that depend on the selected secondary test
method. After satisfying the pretest equilibrium requirements, make
the measurements specified in Table 3 of ASHRAE Standard 37-2009 for
the Indoor Air Enthalpy method and the user-selected secondary
method. Make said Table 3 measurements at equal intervals that span
5 minutes or less. Continue data sampling until a 30-minute period
(e.g., four consecutive 10-minute samples) is reached where the test
tolerances specified in Table 15 are satisfied. For those
continuously recorded parameters, use the entire data set for the
30-minute interval when evaluating Table 15 compliance. Determine
the average electrical power consumption of the heat pump over the
same 30-minute interval.
Table 15--Test Operating and Test Condition Tolerances for Section 3.7
and Section 3.10 Steady-State Heating Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor dry-bulb, [deg]F:
Entering temperature................ 2.0 0.5
Leaving temperature................. 2.0 ..............
Indoor wet-bulb, [deg]F:
Entering temperature................ 1.0 ..............
Leaving temperature................. 1.0 ..............
Outdoor dry-bulb, [deg]F:
Entering temperature................ 2.0 0.5
Leaving temperature................. \2\2.0 ..............
Outdoor wet-bulb, [deg]F:
Entering temperature................ 1.0 0.3
Leaving temperature................. \2\1.0 ..............
External resistance to airflow, inches 0.12 \3\0.02
of water...............................
Electrical voltage, % of rdg............ 2.0 1.5
Nozzle pressure drop, % of rdg.......... 8.0 ..............
------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Only applies when the Outdoor Air Enthalpy Method is used.
\3\ Only applies when testing non-ducted units.
b. Calculate indoor-side total heating capacity as specified in
sections 7.3.4.1 and 7.3.4.3 of ASHRAE Standard 37-2009. Do not
adjust the parameters used in calculating capacity for the permitted
variations in test conditions. Assign the average space heating
capacity and electrical power over the 30-minute data collection
interval to the variables Qh\k\ and
[Edot]h\k\(T) respectively. The ``T'' and superscripted
``k'' are the same as described in section 3.3. Additionally, for
the heating mode, use the superscript to denote results from the
optional H1N Test, if conducted.c. For heat pumps tested
without an indoor blower installed, increase Qh\k\(T) by
[GRAPHIC] [TIFF OMITTED] TP09NO15.240
and increase [Edot]h\k\(T) by,
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
During the 30-minute data collection interval of a High Temperature
Test, pay attention to preventing a defrost cycle. Prior to this
time, allow the heat pump to perform a defrost cycle if
automatically initiated by its own controls. As in all cases, wait
for the heat pump's defrost controls to automatically terminate the
defrost cycle. Heat pumps that undergo a defrost should operate in
the heating mode for at least 10 minutes after defrost termination
prior to beginning the 30-minute data collection interval. For some
heat pumps, frost may accumulate on the outdoor coil during a High
Temperature test. If the indoor coil leaving air temperature or the
difference between the leaving and entering air temperatures
decreases by more than 1.5 [deg]F over the 30-minute data collection
interval, then do not use the collected data to determine capacity.
Instead, initiate a defrost cycle. Begin collecting data no sooner
than 10 minutes after defrost
[[Page 69425]]
termination. Collect 30 minutes of new data during which the Table
15 test tolerances are satisfied. In this case, use only the results
from the second 30-minute data collection interval to evaluate
Qh\k\(47) and [Edot]h\k\(47).
c. For heat pumps tested without an indoor blower installed,
increase Qh\k\(T) by
[GRAPHIC] [TIFF OMITTED] TP09NO15.241
and increase [Edot]h\k\(T) by,
where Vis is the average measured indoor air volume rate
expressed in units of cubic feet per minute of standard air (scfm).
During the 30-minute data collection interval of a High Temperature
Test, pay attention to preventing a defrost cycle. Prior to this
time, allow the heat pump to perform a defrost cycle if
automatically initiated by its own controls. As in all cases, wait
for the heat pump's defrost controls to automatically terminate the
defrost cycle. Heat pumps that undergo a defrost should operate in
the heating mode for at least 10 minutes after defrost termination
prior to beginning the 30-minute data collection interval. For some
heat pumps, frost may accumulate on the outdoor coil during a High
Temperature test. If the indoor coil leaving air temperature or the
difference between the leaving and entering air temperatures
decreases by more than 1.5 [deg]F over the 30-minute data collection
interval, then do not use the collected data to determine capacity.
Instead, initiate a defrost cycle. Begin collecting data no sooner
than 10 minutes after defrost termination. Collect 30 minutes of new
data during which the Table 15 test tolerances are satisfied. In
this case, use only the results from the second 30-minute data
collection interval to evaluate Qh\k\(47) and
[Edot]h\k\(47).
d. If conducting the cyclic heating mode test, which is
described in section 3.8, record the average indoor-side air volume
rate, Vi, specific heat of the air, Cp,a (expressed on
dry air basis), specific volume of the air at the nozzles,
vn' (or vn), humidity ratio at the nozzles,
Wn, and either pressure difference or velocity pressure
for the flow nozzles. If either or both of the below criteria apply,
determine the average, steady-state, electrical power consumption of
the indoor blower motor ([Edot]fan,1):
1. The section 3.8 cyclic test will be conducted and the heat
pump has a variable-speed indoor blower that is expected to be
disabled during the cyclic test; or
2. The heat pump has a (variable-speed) constant-air volume-rate
indoor blower and during the steady-state test the average external
static pressure ([Delta]P1) exceeds the applicable
section 3.1.4.4 minimum (or targeted) external static pressure
([Delta]Pmin) by 0.03 inches of water or more.
Determine [Edot]fan,1 by making measurements during
the 30-minute data collection interval, or immediately following the
test and prior to changing the test conditions. When the above ``2''
criteria applies, conduct the following four steps after determining
[Edot]fan,1 (which corresponds to [Delta]P1):
i. While maintaining the same test conditions, adjust the
exhaust fan of the airflow measuring apparatus until the external
static pressure increases to approximately [Delta]P1 +
([Delta]P1 - [Delta]Pmin).
ii. After re-establishing steady readings for fan motor power
and external static pressure, determine average values for the
indoor blower power ([Edot]fan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
iii. Approximate the average power consumption of the indoor
blower motor if the 30-minute test had been conducted at
[Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TP09NO15.242
iv. Decrease the total space heating capacity,
Qh\k\(T), by the quantity ([Edot]fan,1 -
[Edot]fan,min), when expressed on a Btu/h basis. Decrease
the total electrical power, [Edot]h\k\(T) by the same fan
power difference, now expressed in watts.
e. If the temperature sensors used to provide the primary
measurement of the indoor-side dry bulb temperature difference
during the steady-state dry-coil test and the subsequent cyclic dry-
coil test are different, include measurements of the latter sensors
among the regularly sampled data. Beginning at the start of the 30-
minute data collection period, measure and compute the indoor-side
air dry-bulb temperature difference using both sets of
instrumentation, [Delta]T (Set SS) and [Delta]T (Set CYC), for each
equally spaced data sample. If using a consistent data sampling rate
that is less than 1 minute, calculate and record minutely averages
for the two temperature differences. If using a consistent sampling
rate of one minute or more, calculate and record the two temperature
differences from each data sample. After having recorded the seventh
(i=7) set of temperature differences, calculate the following ratio
using the first seven sets of values:
[GRAPHIC] [TIFF OMITTED] TP09NO15.243
Each time a subsequent set of temperature differences is
recorded (if sampling more frequently than every 5 minutes),
calculate FCD using the most recent seven sets of values.
Continue these calculations until the 30-minute period is completed
or until a value for FCD is calculated that falls outside
the allowable range of 0.94-1.06. If the latter occurs, immediately
suspend the test and
[[Page 69426]]
identify the cause for the disparity in the two temperature
difference measurements. Recalibration of one or both sets of
instrumentation may be required. If all the values for
FCD are within the allowable range, save the final value
of the ratio from the 30-minute test as FCD*. If the
temperature sensors used to provide the primary measurement of the
indoor-side dry bulb temperature difference during the steady-state
dry-coil test and the subsequent cyclic dry-coil test are the same,
set FCD*= 1.
3.8 Test procedures for the cyclic heating mode tests (the
H0C1, H1C, H1C1 and H1C2 Tests).
a. Except as noted below, conduct the cyclic heating mode test
as specified in section 3.5. As adapted to the heating mode, replace
section 3.5 references to ``the steady-state dry coil test'' with
``the heating mode steady-state test conducted at the same test
conditions as the cyclic heating mode test.'' Use the test
tolerances in Table 16 rather than Table 9. Record the outdoor coil
entering wet-bulb temperature according to the requirements given in
section 3.5 for the outdoor coil entering dry-bulb temperature. Drop
the subscript ``dry'' used in variables cited in section 3.5 when
referring to quantities from the cyclic heating mode test. The
default CD value for heating is 0.25. If available, use
electric resistance heaters (see section 2.1) to minimize the
variation in the inlet air temperature. Determine the total space
heating delivered during the cyclic heating test, qcyc,
as specified in section 3.5 except for making the following changes:
(1) When evaluating Equation 3.5-1, use the values of Vi,
Cp,a,vn', (or vn), and
Wn that were recorded during the section 3.7 steady-state
test conducted at the same test conditions.
[GRAPHIC] [TIFF OMITTED] TP09NO15.244
where FCD* is the value recorded during the section 3.7
steady-state test conducted at the same test condition.
b. For ducted heat pumps tested without an indoor blower
installed (excluding the special case where a variable-speed fan is
temporarily removed), increase qcyc by the amount
calculated using Equation 3.5-3. Additionally, increase
ecyc by the amount calculated using Equation 3.5-2. In
making these calculations, use the average indoor air volume rate
(Vis) determined from the section 3.7 steady-state
heating mode test conducted at the same test conditions.
c. For non-ducted heat pumps, subtract the electrical energy
used by the indoor blower during the 3 minutes after compressor
cutoff from the non-ducted heat pump's integrated heating capacity,
qcyc.
d. If a heat pump defrost cycle is manually or automatically
initiated immediately prior to or during the OFF/ON cycling, operate
the heat pump continuously until 10 minutes after defrost
termination. After that, begin cycling the heat pump immediately or
delay until the specified test conditions have been re-established.
Pay attention to preventing defrosts after beginning the cycling
process. For heat pumps that cycle off the indoor blower during a
defrost cycle, make no effort here to restrict the air movement
through the indoor coil while the fan is off. Resume the OFF/ON
cycling while conducting a minimum of two complete compressor OFF/ON
cycles before determining qcyc and ecyc.
3.8.1 Heating mode cyclic-degradation coefficient calculation.
Use the results from the cyclic test and the required steady-
state test that were conducted at the same test conditions to
determine the heating mode cyclic-degradation coefficient
CD\h\. Add ``(k=2)'' to the coefficient if it corresponds
to a two-capacity unit cycling at high capacity. For the below
calculation of the heating mode cyclic degradation coefficient, do
not include the duct loss correction from section 7.3.3.3 of ASHRAE
Standard 37-2009 in determining Qh\k\(Tcyc)
(or qcyc). The tested CD\h\ is calculated as
follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.245
where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.246
the average coefficient of performance during the cyclic heating
mode test, dimensionless.
[GRAPHIC] [TIFF OMITTED] TP09NO15.247
the average coefficient of performance during the steady-state
heating mode test conducted at the same test conditions--i.e., same
outdoor dry bulb temperature, Tcyc, and speed/capacity,
k, if applicable--as specified for the cyclic heating mode test,
dimensionless.
[[Page 69427]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.248
the heating load factor, dimensionless.
Tcyc, the nominal outdoor temperature at which the
cyclic heating mode test is conducted, 62 or 47 [deg]F.
[Delta][tau]cyc, the duration of the OFF/ON
intervals; 0.5 hours when testing a heat pump having a single-speed
or two-capacity compressor and 1.0 hour when testing a heat pump
having a variable-speed compressor.
Round the calculated value for CD\h\ to the nearest
0.01. If CD\h\ is negative, then set it equal to zero.
Table 16--Test Operating and Test Condition Tolerances for Cyclic
Heating Mode Tests
------------------------------------------------------------------------
Test operating Test condition
tolerance \1\ tolerance \1\
------------------------------------------------------------------------
Indoor entering dry-bulb temperature,\2\ 2.0 0.5
[deg]F.................................
Indoor entering wet-bulb temperature,\2\ 1.0 ..............
[deg]F.................................
Outdoor entering dry-bulb 2.0 0.5
temperature,\2\ [deg]F.................
Outdoor entering wet-bulb 2.0 1.0
temperature,\2\ [deg]F.................
External resistance to air-flow,\2\ 0.12 ..............
inches of water........................
Airflow nozzle pressure difference or 2.0 \3\ 2.0
velocity pressure,\2\% of reading......
Electrical voltage,\4\% of rdg.......... 8.0 1.5
------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Applies during the interval that air flows through the indoor
(outdoor) coil except for the first 30 seconds after flow initiation.
For units having a variable-speed indoor blower that ramps, the
tolerances listed for the external resistance to airflow shall apply
from 30 seconds after achieving full speed until ramp down begins.
\3\ The test condition shall be the average nozzle pressure difference
or velocity pressure measured during the steady-state test conducted
at the same test conditions.
\4\ Applies during the interval that at least one of the following--the
compressor, the outdoor fan, or, if applicable, the indoor blower--are
operating, except for the first 30 seconds after compressor start-up.
3.9 Test procedures for Frost Accumulation heating mode tests
(the H2, H22, H2V, and H21 Tests).
a. Confirm that the defrost controls of the heat pump are set as
specified in section 2.2.1. Operate the test room reconditioning
apparatus and the heat pump for at least 30 minutes at the specified
section 3.6 test conditions before starting the ``preliminary'' test
period. The preliminary test period must immediately precede the
``official'' test period, which is the heating and defrost interval
over which data are collected for evaluating average space heating
capacity and average electrical power consumption.
b. For heat pumps containing defrost controls which are likely
to cause defrosts at intervals less than one hour, the preliminary
test period starts at the termination of an automatic defrost cycle
and ends at the termination of the next occurring automatic defrost
cycle. For heat pumps containing defrost controls which are likely
to cause defrosts at intervals exceeding one hour, the preliminary
test period must consist of a heating interval lasting at least one
hour followed by a defrost cycle that is either manually or
automatically initiated. In all cases, the heat pump's own controls
must govern when a defrost cycle terminates.
c. The official test period begins when the preliminary test
period ends, at defrost termination. The official test period ends
at the termination of the next occurring automatic defrost cycle.
When testing a heat pump that uses a time-adaptive defrost control
system (see section 1.2, Definitions), however, manually initiate
the defrost cycle that ends the official test period at the instant
indicated by instructions provided by the manufacturer. If the heat
pump has not undergone a defrost after 6 hours, immediately conclude
the test and use the results from the full 6-hour period to
calculate the average space heating capacity and average electrical
power consumption.
For heat pumps that turn the indoor blower off during the
defrost cycle, take steps to cease forced airflow through the indoor
coil and block the outlet duct whenever the heat pump's controls
cycle off the indoor blower. If it is installed, use the outlet
damper box described in section 2.5.4.1 to affect the blocked outlet
duct.
d. Defrost termination occurs when the controls of the heat pump
actuate the first change in converting from defrost operation to
normal heating operation. Defrost initiation occurs when the
controls of the heat pump first alter its normal heating operation
in order to eliminate possible accumulations of frost on the outdoor
coil.
e. To constitute a valid Frost Accumulation test, satisfy the
test tolerances specified in Table 17 during both the preliminary
and official test periods. As noted in Table 17, test operating
tolerances are specified for two sub-intervals: (1) When heating,
except for the first 10 minutes after the termination of a defrost
cycle (Sub-interval H, as described in Table 17) and (2) when
defrosting, plus these same first 10 minutes after defrost
termination (Sub-interval D, as described in Table 17). Evaluate
compliance with Table 17 test condition tolerances and the majority
of the test operating tolerances using the averages from
measurements recorded only during Sub-interval H. Continuously
record the dry bulb temperature of the air entering the indoor coil,
and the dry bulb temperature and water vapor content of the air
entering the outdoor coil. Sample the remaining parameters listed in
Table 17 at equal intervals that span 5 minutes or less.
f. For the official test period, collect and use the following
data to calculate average space heating capacity and electrical
power. During heating and defrosting intervals when the controls of
the heat pump have the indoor blower on, continuously record the
dry-bulb temperature of the air entering (as noted above) and
leaving the indoor coil. If using a thermopile, continuously record
the difference between the leaving and entering dry-bulb
temperatures during the interval(s) that air flows through the
indoor coil. For heat pumps tested without an indoor blower
installed, determine the corresponding cumulative time (in hours) of
indoor coil airflow, [Delta][tau]a. Sample measurements
used in calculating the air volume rate (refer to sections 7.7.2.1
and 7.7.2.2 of ASHRAE Standard 37-2009) at equal intervals that span
10 minutes or less. (Note: In the first printing of ASHRAE Standard
37-2009, the second IP equation for Qmi should read:
[[Page 69428]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.249
Record the electrical energy consumed, expressed in watt-hours, from
defrost termination to defrost termination, eDEF\k\(35),
as well as the corresponding elapsed time in hours,
[Delta][tau]FR.
Table 17--Test Operating and Test Condition Tolerances for Frost Accumulation Heating Mode Tests
----------------------------------------------------------------------------------------------------------------
Test operating tolerance \1\ Test condition
-------------------------------- tolerance \1\
Sub-interval H Sub-interval D Sub-interval H
\2\ \3\ \2\
----------------------------------------------------------------------------------------------------------------
Indoor entering dry-bulb temperature, [deg]F.................... 2.0 \4\ 4.0 0.5
Indoor entering wet-bulb temperature, [deg]F.................... 1.0 .............. ..............
Outdoor entering dry-bulb temperature, [deg]F................... 2.0 10.0 1.0
Outdoor entering wet-bulb temperature, [deg]F................... 1.5 .............. 0.5
External resistance to airflow, inches of water................. 0.12 .............. \5\ 0.02
Electrical voltage, % of rdg.................................... 2.0 .............. 1.5
----------------------------------------------------------------------------------------------------------------
\1\ See section 1.2, Definitions.
\2\ Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a
defrost cycle.
\3\ Applies during a defrost cycle and during the first 10 minutes after the termination of a defrost cycle when
the heat pump is operating in the heating mode.
\4\ For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies
during the 10 minute interval that follows defrost termination.
\5\ Only applies when testing non-ducted heat pumps.
3.9.1 Average space heating capacity and electrical power
calculations.
a. Evaluate average space heating capacity,
Qh\k\(35), when expressed in units of Btu per hour,
using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.250
Where,
Vi = the average indoor air volume rate measured during Sub-interval
H, cfm.
Cp,a = 0.24 + 0.444 [middot] Wn, the constant
pressure specific heat of the air-water vapor mixture that flows
through the indoor coil and is expressed on a dry air basis, Btu/
lbmda [middot] [deg]F.
vn' = specific volume of the air-water vapor mixture at
the nozzle, ft\3\/lbmmx.
Wn = humidity ratio of the air-water vapor mixture at the
nozzle, lbm of water vapor per lbm of dry air.
[Delta][tau]FR = [tau]2 - [tau]1,
the elapsed time from defrost termination to defrost termination,
hr.
[GRAPHIC] [TIFF OMITTED] TP09NO15.251
Tal([tau]) = dry bulb temperature of the air entering the
indoor coil at elapsed time [tau], [deg]F; only recorded when indoor
coil airflow occurs; assigned the value of zero during periods (if
any) where the indoor blower cycles off.
Ta2([tau]) = dry bulb temperature of the air leaving the
indoor coil at elapsed time [tau], [deg]F; only recorded when indoor
coil airflow occurs; assigned the value of zero during periods (if
any) where the indoor blower cycles off.
[tau]1 = the elapsed time when the defrost termination
occurs that begins the official test period, hr.
[tau]2 = the elapsed time when the next automatically
occurring defrost termination occurs, thus ending the official test
period, hr.
vn = specific volume of the dry air portion of the
mixture evaluated at the dry-bulb temperature, vapor content, and
barometric pressure existing at the nozzle, ft\3\ per lbm of dry
air.
To account for the effect of duct losses between the outlet of
the indoor unit and the section 2.5.4 dry-bulb temperature grid,
adjust Qh\k\(35) in accordance with section 7.3.4.3 of
ASHRAE Standard 37-2009.
b. Evaluate average electrical power, [Edot]h\k\(35),
when expressed in units of watts, using:
[[Page 69429]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.252
For heat pumps tested without an indoor blower installed,
increase Qh\k\(35) by,
[GRAPHIC] [TIFF OMITTED] TP09NO15.253
where Vis is the average indoor air volume rate measured
during the Frost Accumulation heating mode test and is expressed in
units of cubic feet per minute of standard air (scfm).
c. For heat pumps having a constant-air-volume-rate indoor
blower, the five additional steps listed below are required if the
average of the external static pressures measured during sub-
Interval H exceeds the applicable section 3.1.4.4, 3.1.4.5, or
3.1.4.6 minimum (or targeted) external static pressure
([Delta]Pmin) by 0.03 inches of water or more:
1. Measure the average power consumption of the indoor blower
motor ([Edot]fan,1) and record the corresponding external
static pressure ([Delta]P1) during or immediately
following the Frost Accumulation heating mode test. Make the
measurement at a time when the heat pump is heating, except for the
first 10 minutes after the termination of a defrost cycle.
2. After the Frost Accumulation heating mode test is completed
and while maintaining the same test conditions, adjust the exhaust
fan of the airflow measuring apparatus until the external static
pressure increases to approximately [Delta]P1 +
([Delta]P1 - [Delta]Pmin).
3. After re-establishing steady readings for the fan motor power
and external static pressure, determine average values for the
indoor blower power ([Edot]fan,2) and the external static
pressure ([Delta]P2) by making measurements over a 5-
minute interval.
4. Approximate the average power consumption of the indoor
blower motor had the Frost Accumulation heating mode test been
conducted at [Delta]Pmin using linear extrapolation:
[GRAPHIC] [TIFF OMITTED] TP09NO15.254
5. Decrease the total heating capacity, Qh\k\(35), by
the quantity [([Edot]fan,1 -
[Edot]fan,min)[middot] ([Delta][tau] a/
[Delta][tau]FR], when expressed on a Btu/h basis.
Decrease the total electrical power, Eh\k\(35), by the
same quantity, now expressed in watts.
3.9.2 Demand defrost credit.
a. Assign the demand defrost credit, Fdef, that is
used in section 4.2 to the value of 1 in all cases except for heat
pumps having a demand-defrost control system (see section 1.2,
Definitions). For such qualifying heat pumps, evaluate
Fdef using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.255
Where,
[Delta][tau]def = the time between defrost terminations
(in hours) or 1.5, whichever is greater. A value of 6 must be
assigned to [Delta][tau]def if this limit is reached
during a Frost Accumulation test and the heat pump has not completed
a defrost cycle.
[Delta][tau]max = maximum time between defrosts as
allowed by the controls (in hours) or 12, whichever is less, as
provided in the installation manuals included with the unit by the
manufacturer.
b. For two-capacity heat pumps and for section 3.6.2 units,
evaluate the above equation using the [Delta][tau]def
that applies based on the Frost Accumulation Test conducted at high
capacity and/or at the Heating Full-load Air Volume Rate. For
variable-speed heat pumps, evaluate [Delta][tau]def based
on the required Frost Accumulation Test conducted at the
intermediate compressor speed.
3.10 Test procedures for steady-state Low Temperature heating
mode tests (the H3, H32, H31 and
H42 Tests).
Except for the modifications noted in this section, conduct the
Low Temperature heating mode test using the same approach as
specified in section 3.7 for the Maximum and High Temperature tests.
After satisfying the section 3.7 requirements for the pretest
[[Page 69430]]
interval but before beginning to collect data to determine
Qh\k\(17) and [Edot]h\k\(17), conduct a
defrost cycle. This defrost cycle may be manually or automatically
initiated. The defrost sequence must be terminated by the action of
the heat pump's defrost controls. Begin the 30-minute data
collection interval described in section 3.7, from which
Qh\k\(17) and [Edot]h\k\(17) are determined,
no sooner than 10 minutes after defrost termination. Defrosts should
be prevented over the 30-minute data collection interval. Defrost
cycle is not required for H42 Test.
3.11 Additional requirements for the secondary test methods.
3.11.1 If using the Outdoor Air Enthalpy Method as the secondary
test method.
During the ``official'' test, the outdoor air-side test
apparatus described in section 2.10.1 is connected to the outdoor
unit. To help compensate for any effect that the addition of this
test apparatus may have on the unit's performance, conduct a
``preliminary'' test where the outdoor air-side test apparatus is
disconnected. Conduct a preliminary test prior to the first section
3.2 steady-state cooling mode test and prior to the first section
3.6 steady-state heating mode test. No other preliminary tests are
required so long as the unit operates the outdoor fan during all
cooling mode steady-state tests at the same speed and all heating
mode steady-state tests at the same speed. If using more than one
outdoor fan speed for the cooling mode steady-state tests, however,
conduct a preliminary test prior to each cooling mode test where a
different fan speed is first used. This same requirement applies for
the heating mode tests.
3.11.1.1 If a preliminary test precedes the official test.
a. The test conditions for the preliminary test are the same as
specified for the official test. Connect the indoor air-side test
apparatus to the indoor coil; disconnect the outdoor air-side test
apparatus. Allow the test room reconditioning apparatus and the unit
being tested to operate for at least one hour. After attaining
equilibrium conditions, measure the following quantities at equal
intervals that span 5 minutes or less:
1. The section 2.10.1 evaporator and condenser temperatures or
pressures;
2. Parameters required according to the Indoor Air Enthalpy
Method.
Continue these measurements until a 30-minute period (e.g., four
consecutive 10-minute samples) is obtained where the Table 8 or
Table 15, whichever applies, test tolerances are satisfied.
b. After collecting 30 minutes of steady-state data, reconnect
the outdoor air-side test apparatus to the unit. Adjust the exhaust
fan of the outdoor airflow measuring apparatus until averages for
the evaporator and condenser temperatures, or the saturated
temperatures corresponding to the measured pressures, agree within
0.5 [deg]F of the averages achieved when the outdoor
air-side test apparatus was disconnected. Calculate the averages for
the reconnected case using five or more consecutive readings taken
at one minute intervals. Make these consecutive readings after re-
establishing equilibrium conditions and before initiating the
official test.
3.11.1.2 If a preliminary test does not precede the official
test.
Connect the outdoor-side test apparatus to the unit. Adjust the
exhaust fan of the outdoor airflow measuring apparatus to achieve
the same external static pressure as measured during the prior
preliminary test conducted with the unit operating in the same
cooling or heating mode at the same outdoor fan speed.
3.11.1.3 Official test.
a. Continue (preliminary test was conducted) or begin (no
preliminary test) the official test by making measurements for both
the Indoor and Outdoor Air Enthalpy Methods at equal intervals that
span 5 minutes or less. Discontinue these measurements only after
obtaining a 30-minute period where the specified test condition and
test operating tolerances are satisfied. To constitute a valid
official test:
(1) Achieve the energy balance specified in section 3.1.1; and,
(2) For cases where a preliminary test is conducted, the
capacities determined using the Indoor Air Enthalpy Method from the
official and preliminary test periods must agree within 2.0 percent.
b. For space cooling tests, calculate capacity from the outdoor
air-enthalpy measurements as specified in sections 7.3.3.2 and
7.3.3.3 of ASHRAE Standard 37-2009. Calculate heating capacity based
on outdoor air-enthalpy measurements as specified in sections
7.3.4.2 and 7.3.3.4.3 of the same ASHRAE Standard. Adjust the
outdoor-side capacity according to section 7.3.3.4 of ASHRAE
Standard 37-2009 to account for line losses when testing split
systems. Use the outdoor unit fan power as measured during the
official test and not the value measured during the preliminary
test, as described in section 8.6.2 of ASHRAE Standard 37-2009, when
calculating the capacity.
3.11.2 If using the Compressor Calibration Method as the
secondary test method.
a. Conduct separate calibration tests using a calorimeter to
determine the refrigerant flow rate. Or for cases where the
superheat of the refrigerant leaving the evaporator is less than 5
[deg]F, use the calorimeter to measure total capacity rather than
refrigerant flow rate. Conduct these calibration tests at the same
test conditions as specified for the tests in this appendix. Operate
the unit for at least one hour or until obtaining equilibrium
conditions before collecting data that will be used in determining
the average refrigerant flow rate or total capacity. Sample the data
at equal intervals that span 5 minutes or less. Determine average
flow rate or average capacity from data sampled over a 30-minute
period where the Table 8 (cooling) or the Table 15 (heating)
tolerances are satisfied. Otherwise, conduct the calibration tests
according to sections 5, 6, 7, and 8 of ASHRAE Standard 23.1-2010;
sections 5, 6, 7, 8, 9, and 11 of ASHRAE Standard 41.9-2011; and
section 7.4 of ASHRAE Standard 37-2009 (incorporated by reference,
see Sec. 430.3).
b. Calculate space cooling and space heating capacities using
the compressor calibration method measurements as specified in
section 7.4.5 and 7.4.6 respectively, of ASHRAE Standard 37-2009.
3.11.3 If using the Refrigerant-Enthalpy Method as the secondary
test method.
Conduct this secondary method according to section 7.5 of ASHRAE
Standard 37-2009. Calculate space cooling and heating capacities
using the refrigerant-enthalpy method measurements as specified in
sections 7.5.4 and 7.5.5, respectively, of the same ASHRAE Standard.
3.12 Rounding of space conditioning capacities for reporting
purposes.
a. When reporting rated capacities, round them off as specified
in 10 CFR 430.23 (for a single unit) and in 10 CFR 429.16 (for a
sample).
b. For the capacities used to perform the section 4
calculations, however, round only to the nearest integer.
3.13 Laboratory testing to determine off mode average power
ratings.
Conduct one of the following tests after the completion of the
B, B1, or B2 Test, whichever comes last: If
the central air conditioner or heat pump lacks a compressor
crankcase heater, perform the test in section 3.13.1; if the central
air conditioner or heat pump has compressor crankcase heater that
lacks controls, perform the test in section 3.13.1; if the central
air conditioner or heat pump has a compressor crankcase heater
equipped with controls, perform the test in section 3.13.2.
3.13.1 This test determines the off mode average power rating
for central air conditioners and heat pumps that lack a compressor
crankcase heater, or have a compressor crankcase heater that lacks
controls.
a. Configure Controls: Configure the controls of the central air
conditioner or heat pump so that it operates as if connected to a
building thermostat that is set to the OFF position. This particular
test contains no requirements as to ambient conditions within the
test rooms, and room conditions are allowed to change during the
test. Ensure that the low-voltage transformer and low-voltage
components are connected.
b. Measure P1x: Determine the average power from non-zero value
data measured over a 5-minute interval of the non-operating central
air conditioner or heat pump and designate the average power as P1x,
the shoulder season total off mode power.
c. Measure Px for coil-only split systems (that would be
installed in the field with a furnace having a dedicated board for
indoor controls) and for blower-coil split systems for which a
furnace is the designated air mover: Disconnect all low-voltage
wiring for the outdoor components and outdoor controls from the low-
voltage transformer. Determine the average power from non-zero value
data measured over a 5-minute interval of the power supplied to the
(remaining) low-voltage components of the central air conditioner or
heat pump, or low-voltage power, Px.
d. Calculate P1:
Single-package systems and blower coil split systems for which
the designated air mover is not a furnace: Divide the shoulder
season total off mode power (P1x) by the number of compressors to
calculate P1, the
[[Page 69431]]
shoulder season per-compressor off mode power. If the compressor is
a modulating-type, assign a value of 1.5 for the number of
compressors. Round P1 to the nearest watt and record as both P1 and
P2, the latter of which is the heating season per-compressor off
mode power. The expression for calculating P1 is as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.256
Coil-only split systems (that would be installed in the field
with a furnace having a dedicated board for indoor controls) and
blower-coil split systems for which a furnace is the designated air
mover: Subtract the low-voltage power (Px) from the shoulder season
total off mode power (P1x) and divide by the number of compressors
to calculate P1, the shoulder season per-compressor off mode power.
If the compressor is a modulating-type, assign a value of 1.5 for
the number of compressors. Round P1 to the nearest watt and record
as both P1 and P2, the latter of which is the heating season per-
compressor off mode power. The expression for calculating P1 is as
follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.257
3.13.2 This test determines the off mode average power rating
for central air conditioners and heat pumps that have a compressor
crankcase heater equipped with controls.
a. Configure Controls: Position a temperature sensor to measure
the outdoor dry-bulb temperature in the air between 2 and 6 inches
from the crankcase heater temperature sensor or, if no such
temperature sensor exists, position it in the air between 2 and 6
inches from the crankcase heater. Utilize the temperature
measurements from this sensor for this portion of the test
procedure. Configure the controls of the central air conditioner or
heat pump so that it operates as if connected to a building
thermostat that is set to the OFF position. Ensure that the low-
voltage transformer and low-voltage components are connected. Adjust
the outdoor temperature at a rate of change of no more than 20
[deg]F per hour and achieve an outdoor dry-bulb temperature of 72
[deg]F. Maintain this temperature within 2 [deg]F for at
least 5 minutes, while maintaining an indoor dry-bulb temperature of
between 75 [deg]F and 85 [deg]F.
b. Measure P1x: Determine the average power from non-zero value
data measured over a 5-minute interval of the non-operating central
air conditioner or heat pump and designate the average power as P1x,
the shoulder season total off mode power.
c. Reconfigure Controls: In the process of reaching the target
outdoor dry-bulb temperature, adjust the outdoor temperature at a
rate of change of no more than 20 [deg]F per hour. This target
temperature is the temperature specified by the manufacturer in the
DOE Compliance Certification Database at which the crankcase heater
turns on, minus five degrees Fahrenheit. Maintain this temperature
within 2 [deg]F for at least 5 minutes, while
maintaining an indoor dry-bulb temperature of between 75 [deg]F and
85 [deg]F.
d. Measure P2x: Determine the average non-zero power of the non-
operating central air conditioner or heat pump over a 5-minute
interval and designate it as P2x, the heating season total off mode
power.
e. Measure Px for coil-only split systems (that would be
installed in the field with a furnace having a dedicated board for
indoor controls) and for blower-coil split systems for which a
furnace is the designated air mover: Disconnect all low-voltage
wiring for the outdoor components and outdoor controls from the low-
voltage transformer. Determine the average power from non-zero value
data measured over a 5-minute interval of the power supplied to the
(remaining) low-voltage components of the central air conditioner or
heat pump, or low-voltage power, Px
f. Calculate P1:
Single-package systems and blower coil split systems for which
the air mover is not a furnace: Divide the shoulder season total off
mode power (P1x) by the number of compressors to calculate P1, the
shoulder season per-compressor off mode power. Round to the nearest
watt. If the compressor is a modulating-type, assign a value of 1.5
for the number of compressors. The expression for calculating P1 is
as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.258
Coil-only split systems (that would be installed in the field
with a furnace having a dedicated board for indoor controls) and
blower-coil split systems for which a furnace is the designated air
mover: Subtract the low-voltage power (Px) from the shoulder season
total off mode power (P1x) and divide by the number of compressors
to calculate P1, the shoulder season per-compressor off mode power.
Round to the nearest watt. If the compressor is a modulating-type,
assign a value of 1.5 for the number of compressors. The expression
for calculating P1 is as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.259
[[Page 69432]]
h. Calculate P2:
Single-package systems and blower coil split systems for which
the air mover is not a furnace: Divide the heating season total off
mode power (P2x) by the number of compressors to calculate P2, the
heating season per-compressor off mode power. Round to the nearest
watt. If the compressor is a modulating-type, assign a value of 1.5
for the number of compressors. The expression for calculating P2 is
as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.260
Coil-only split systems (that would be installed in the field
with a furnace having a dedicated board for indoor controls) and
blower-coil split systems for which a furnace is the designated air
mover: Subtract the low-voltage power (Px) from the heating season
total off mode power (P2x) and divide by the number of compressors
to calculate P2, the heating season per-compressor off mode power.
Round to the nearest watt. If the compressor is a modulating-type,
assign a value of 1.5 for the number of compressors. The expression
for calculating P2 is as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.261
4. Calculations of Seasonal Performance Descriptors
4.1 Seasonal Energy Efficiency Ratio (SEER) Calculations. SEER
must be calculated as follows: For equipment covered under sections
4.1.2, 4.1.3, and 4.1.4, evaluate the seasonal energy efficiency
ratio,
[[Page 69433]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.262
where,
Qc\k=2\(95) = the space cooling capacity determined from
the A2 Test and calculated as specified in section 3.3,
Btu/h.
1.1 = sizing factor, dimensionless.
The temperatures 95 [deg]F and 65 [deg]F in the building load
equation represent the selected outdoor design temperature and the
zero-load base temperature, respectively.
4.1.1 SEER calculations for an air conditioner or heat pump
having a single-speed compressor that was tested with a fixed-speed
indoor blower installed, a constant-air-volume-rate indoor blower
installed, or with no indoor blower installed.
a. Evaluate the seasonal energy efficiency ratio, expressed in
units of Btu/watt-hour, using:
SEER = PLF (0.5) * EERB
Where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.263
[[Page 69434]]
PLF(0.5) = 1 - 0.5 [middot] CD\c\, the part-load
performance factor evaluated at a cooling load factor of 0.5,
dimensionless.
b. Refer to section 3.3 regarding the definition and calculation
of Qc(82) and [Edot]c(82).
4.1.2 SEER calculations for an air conditioner or heat pump
having a single-speed compressor and a variable-speed variable-air-
volume-rate indoor blower.
4.1.2.1 Units covered by section 3.2.2.1 where indoor blower
capacity modulation correlates with the outdoor dry bulb
temperature. The manufacturer must provide information on how the
indoor air volume rate or the indoor blower speed varies over the
outdoor temperature range of 67 [deg]F to 102 [deg]F. Calculate SEER
using Equation 4.1-1. Evaluate the quantity
qc(Tj)/N in Equation 4.1-1 using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.264
Qc(Tj) = the space cooling capacity of the
test unit when operating at outdoor temperature, Tj, Btu/
h.
nj/N = fractional bin hours for the cooling season; the
ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless.
a. For the space cooling season, assign nj/N as
specified in Table 18. Use Equation 4.1-2 to calculate the building
load, BL(Tj). Evaluate Qc(Tj)
using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.265
the space cooling capacity of the test unit at outdoor temperature
Tj if operated at the Cooling Minimum Air Volume Rate,
Btu/h.
[GRAPHIC] [TIFF OMITTED] TP09NO15.266
the space cooling capacity of the test unit at outdoor temperature
Tj if operated at the Cooling Full-load Air Volume Rate,
Btu/h.
b. For units where indoor blower speed is the primary control
variable, FPc\k=1\ denotes the fan speed used during the
required A1 and B1 Tests (see section
3.2.2.1), FPc\k=2\ denotes the fan speed used during the
required A2 and B2 Tests, and
FPc(Tj) denotes the fan speed used by the unit
when the outdoor temperature equals Tj. For units where
indoor air volume rate is the primary control variable, the three
FPc's are similarly defined only now being expressed in
terms of air volume rates rather than fan speeds. Refer to sections
3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 regarding the definitions and
calculations of Qc\k=1\(82), Qc\k=1\(95),
Qc \k=2\(82), and Qc\k=2\(95).
[GRAPHIC] [TIFF OMITTED] TP09NO15.267
Where,
PLFj = 1 - CD\c\ [middot] [1 -
X(Tj)], the part load factor, dimensionless.
[Edot]c(Tj) = the electrical power consumption
of the test unit when operating at outdoor temperature
Tj, W.
c. The quantities X(Tj) and nj/N are the
same quantities as used in Equation 4.1.2-1.
d. Evaluate [Edot]c(Tj) using,
[[Page 69435]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.268
the electrical power consumption of the test unit at outdoor
temperature Tj if operated at the Cooling Full-load Air
Volume Rate, W.
e. The parameters FPc\k=1\, and FPc\k=2\,
and FPc(Tj) are the same quantities that are
used when evaluating Equation 4.1.2-2. Refer to sections 3.2.2.1,
3.1.4 to 3.1.4.2, and 3.3 regarding the definitions and calculations
of [Edot]c\k=1\(82), [Edot]c\k=1\(95),
[Edot]c\k=2\(82), and [Edot]c\k=2\(95).
4.1.2.2 Units covered by section 3.2.2.2 where indoor blower
capacity modulation is used to adjust the sensible to total cooling
capacity ratio. Calculate SEER as specified in section 4.1.1.
4.1.3 SEER calculations for an air conditioner or heat pump
having a two-capacity compressor. Calculate SEER using Equation 4.1-
1. Evaluate the space cooling capacity,
Qc\k=1\(Tj), and electrical power consumption,
[Edot]c\k=1\(Tj), of the test unit when
operating at low compressor capacity and outdoor temperature
Tj using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.269
where Qc\k=1\(82) and [Edot]c\k=1\(82) are
determined from the B1 Test, Qc\k=1\(67) and
[Edot]c\k=1\(67) are determined from the
F1Test, and all four quantities are calculated as
specified in section 3.3. Evaluate the space cooling capacity,
Qc\k=2\(Tj), and electrical power consumption,
[Edot]c\k=2\(Tj), of the test unit when
operating at high compressor capacity and outdoor temperature
Tj using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.501
where Qc\k=2\(95) and [Edot]c\k=2\(95) are
determined from the A2 Test, Qc\k=2\(82), and
[Edot]c\k=2\(82), are determined from the
B2Test, and all are calculated as specified in section
3.3.
The calculation of Equation 4.1-1 quantities
qc(Tj)/N and ec(Tj)/N
differs depending on whether the test unit would operate at low
capacity (section 4.1.3.1), cycle between low and high capacity
(section 4.1.3.2), or operate at high capacity (sections 4.1.3.3 and
4.1.3.4) in responding to the building load. For units that lock out
low capacity operation at higher outdoor temperatures, the
manufacturer must supply information regarding this temperature so
that the appropriate equations are used. Use Equation 4.1-2 to
calculate the building load, BL(Tj), for each temperature
bin.
4.1.3.1 Steady-state space cooling capacity at low compressor
capacity is greater than or equal to the building cooling load at
temperature Tj, Qc\k=1\(Tj)
>=BL(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.270
Where,
X\k=1\(Tj) = BL(Tj)/
Qc\k=1\(Tj), the cooling mode low capacity
load factor for temperature bin j, dimensionless.
PLFj = 1 - CD\c\ [middot] [1 -
X\k=1\(Tj)], the part load factor, dimensionless.
nj/N, the fractional bin hours for the cooling season;
the ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless. Obtain the fractional bin hours for
the cooling season, nj/N, from Table 18. Use Equations
4.1.3-1 and 4.1.3-2, respectively, to evaluate
Qc\k=1\(Tj) and
[Edot]c\k=1\(Tj).
[[Page 69436]]
Table 18--Distribution of Fractional Hours Within Cooling Season Temperature Bins
----------------------------------------------------------------------------------------------------------------
Fraction of of
Bin Representative total
Bin number, j temperature temperature temperature
range [deg]F for bin [deg]F bin hours, nj/
N
----------------------------------------------------------------------------------------------------------------
1............................................................... 65-69 67 0.214
2............................................................... 70-74 72 0.231
3............................................................... 75-79 77 0.216
4............................................................... 80-84 82 0.161
5............................................................... 85-89 87 0.104
6............................................................... 90-94 92 0.052
7............................................................... 95-99 97 0.018
8............................................................... 100-104 102 0.004
----------------------------------------------------------------------------------------------------------------
4.1.3.2 Unit alternates between high (k=2) and low (k=1)
compressor capacity to satisfy the building cooling load at
temperature Tj, Qc\k=1\(Tj)
j) c\k=2\(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.271
X\k=2\(Tj) = 1 - X\k=1\(Tj), the cooling mode,
high capacity load factor for temperature bin j, dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 18. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qc\k=1\(Tj) and
[Edot]c\k=1\(Tj). Use Equations 4.1.3-3 and
4.1.3-4, respectively, to evaluate Qc\k=2\(Tj)
and [Edot]c\k=2\(Tj).
4.1.3.3 Unit only operates at high (k=2) compressor capacity at
temperature Tj and its capacity is greater than the
building cooling load, BL(Tj)
c\k=2\(Tj). This section applies to units
that lock out low compressor capacity operation at higher outdoor
temperatures.
[GRAPHIC] [TIFF OMITTED] TP09NO15.272
where,
X\k=2\(Tj) = BL(Tj)/
Qc\k=2\(Tj), the cooling mode high capacity
load factor for temperature bin j, dimensionless.
PLFj = 1-[Cdot]D(\k=2\) * [1-
X\k=2\(Tj)], the part load factor, dimensionless.
[GRAPHIC] [TIFF OMITTED] TP09NO15.273
4.1.3.4 Unit must operate continuously at high (k=2) compressor
capacity at temperature Tj, BL(Tj)
>=Qc\k=2\(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.274
[[Page 69437]]
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 18. Use Equations 4.1.3-3 and 4.1.3-4,
respectively, to evaluate Qc\k=2\(Tj) and
[Edot]c\k=2\(Tj).
4.1.4 SEER calculations for an air conditioner or heat pump
having a variable-speed compressor. Calculate SEER using Equation
4.1-1. Evaluate the space cooling capacity,
Qc\k=1\(Tj), and electrical power consumption,
[Edot]c\k=1\(Tj), of the test unit when
operating at minimum compressor speed and outdoor temperature
Tj. Use,
[GRAPHIC] [TIFF OMITTED] TP09NO15.502
where Qc\k=1\(82) and [Edot]c\k=1\(82) are
determined from the B1 Test, Qc\k=1\(67) and
[Edot]c\k=1\(67) are determined from the F1 Test, and all
four quantities are calculated as specified in section 3.3. Evaluate
the space cooling capacity, Qc\k=2\(Tj), and
electrical power consumption,
[Edot]c\k=2\(Tj), of the test unit when
operating at maximum compressor speed and outdoor temperature
Tj. Use Equations 4.1.3-3 and 4.1.3-4, respectively,
where Qc\k=2\(95) and [Edot]c\k=2\(95) are
determined from the A2 Test, Qc\k=2\(82) and
[Edot]c\k=2\(82) are determined from the B2
Test, and all four quantities are calculated as specified in section
3.3. Calculate the space cooling capacity,
Qc\k=v\(Tj), and electrical power consumption,
[Edot]c\k=v\(Tj), of the test unit when
operating at outdoor temperature Tj and the intermediate
compressor speed used during the section 3.2.4 (and Table 7)
EV Test using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.275
4.1.4.1 Steady-state space cooling capacity when operating at
minimum compressor speed is greater than or equal to the building
cooling load at temperature Tj,
Qc\k=1\(Tj) >=BL(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.276
where,
X\k=1\(Tj) = BL(Tj)/
Qc\k=1\(Tj), the cooling mode minimum speed
load factor for temperature bin j, dimensionless.
PLFj = 1 - CD\c\ [middot] [1 -
X\k=1\(Tj)], the part load factor, dimensionless.
nj/N, the fractional bin hours for the cooling season;
the ratio of the number of hours during the cooling season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
cooling season, dimensionless.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 18. Use Equations 4.1.3-1 and 4.1.3-2,
respectively, to evaluate Qc\k=l\ (Tj) and
[Edot]c\k=l\ (Tj).
4.1.4.2 Unit operates at an intermediate compressor speed (k=i)
in order to match the building cooling load at temperature
Tj,Qc\k=1\(Tj) j)
c\k=2\(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.277
where,
Qc\k=i\(Tj) = BL(Tj), the space
cooling capacity delivered by the unit in matching the building load
at temperature Tj, Btu/h. The matching occurs with the
unit operating at compressor speed k = i.
[GRAPHIC] [TIFF OMITTED] TP09NO15.278
EER\k=i\(Tj) = the steady-state energy efficiency ratio
of the test unit when operating at a compressor speed of k = i and
temperature Tj, Btu/h per W.
Obtain the fractional bin hours for the cooling season,
nj/N, from Table 18. For each
[[Page 69438]]
temperature bin where the unit operates at an intermediate
compressor speed, determine the energy efficiency ratio
EER\k=i\(Tj) using,
EER\k=i\(Tj) = A + B [middot] Tj + C [middot]
Tj\2\.
For each unit, determine the coefficients A, B, and C by
conducting the following calculations once:
[GRAPHIC] [TIFF OMITTED] TP09NO15.279
where,
T1 = the outdoor temperature at which the unit, when
operating at minimum compressor speed, provides a space cooling
capacity that is equal to the building load (Qc\k=l\
(Tl) = BL(T1)), [deg]F. Determine
T1 by equating Equations 4.1.3-1 and 4.1-2 and solving
for outdoor temperature.
Tv = the outdoor temperature at which the unit, when
operating at the intermediate compressor speed used during the
section 3.2.4 EV Test, provides a space cooling capacity
that is equal to the building load (Qc\k=v\
(Tv) = BL(Tv)), [deg]F. Determine
Tv by equating Equations 4.1.4-1 and 4.1-2 and solving
for outdoor temperature.
T2 = the outdoor temperature at which the unit, when
operating at maximum compressor speed, provides a space cooling
capacity that is equal to the building load (Qc\k=2\
(T2) = BL(T2)), [deg]F. Determine
T2 by equating Equations 4.1.3-3 and 4.1-2 and solving
for outdoor temperature.
[GRAPHIC] [TIFF OMITTED] TP09NO15.280
4.1.4.3 Unit must operate continuously at maximum (k=2)
compressor speed at temperature Tj, BL(Tj)
>=Qc\k=2\(Tj). Evaluate the Equation 4.1-1
quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.281
as specified in section 4.1.3.4 with the understanding that
Qc\k=2\(Tj) and
[Edot]c\k=2\(Tj) correspond to maximum
compressor speed operation and are derived from the results of the
tests specified in section 3.2.4.
4.1.5 SEER calculations for an air conditioner or heat pump
having a single indoor unit with multiple blowers. Calculate SEER
using Eq. 4.1-1, where qc(Tj)/N and ec(Tj)/N
are evaluated as specified in applicable below subsection.
4.1.5.1 For multiple blower systems that are connected to a
lone, single-speed outdoor unit. a. Calculate the space cooling
capacity, Qck\=1\ (Tj), and electrical power consumption,
[Edot]ck\=1\ (Tj), of the test unit when operating at the cooling
minimum air volume rate and outdoor temperature Tj using
the equations given in section 4.1.2.1. Calculate the space cooling
capacity, Qck\=2\ (Tj), and electrical power consumption,
[Edot]ck\=2\ (Tj), of the test unit when operating at the cooling
full-load air volume rate and outdoor temperature Tj
using the equations given in section 4.1.2.1. In evaluating the
section 4.1.2.1 equations, determine the quantities Qck\=1\ (82) and
[Edot]ck\=1\ (82) from the B1 Test, Qck\=1\ (95) and [Edot]ck\=1\
(95) from the Al Test, Qck\=2\ (82) and [Edot]ck\=2\ (82) from the
B2 Test, and Qck\=2\ (95) and [Edot]ck\=2\ (95) from the A2 Test.
Evaluate all eight quantities as specified in section 3.3. Refer to
section 3.2.2.1 and Table 5 for additional information on the four
referenced laboratory tests. b. Determine the cooling mode cyclic
degradation coefficient, CDc, as per sections 3.2.2.1 and
3.5 to 3.5.3. Assign this same value to CDc(K=2). c.
Except for using the above values of Qck\=1\ (Tj), [Edot]ck\=1\
(Tj), [Edot]ck\=2\ (Tj), Qck\=2\ (Tj), CDc, and
CDc (K=2), calculate the quantities
qc(Tj)/N and ec(Tj)/N as
specified in section 4.1.3.1 for cases where Qck\=1\ (Tj) >=
BL(Tj). For all other outdoor bin temperatures,
Tj, calculate qc(Tj)/N and ec(Tj)/N
as specified in section 4.1.3.3 if Qck\=2\ (Tj) > BL (Tj)
or as specified in section 4.1.3.4 if Qck\=2\ (Tj) <=
BL(Tj).
4.1.5.2 For multiple blower systems that are connected to either
a lone outdoor unit having a two-capacity compressor or to two
separate but identical model single-speed outdoor units. Calculate
the quantities qc(Tj)/N and ec(Tj)/N as
specified in section 4.1.3.
4.2 Heating Seasonal Performance Factor (HSPF) Calculations.
Unless an approved alternative efficiency determination method
is used, as set forth in 10 CFR 429.70(e), HSPF must be calculated
as follows: Six generalized climatic regions are depicted in Figure
1 and otherwise defined in Table 19. For each of these regions and
for each applicable standardized design heating requirement,
evaluate the heating seasonal performance factor using,
[[Page 69439]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.282
Where,
eh(Tj)/N, the ratio of the electrical
energy consumed by the heat pump during periods of the space heating
season when the outdoor temperature fell within the range
represented by bin temperature Tj to the total number of
hours in the heating season (N), W. For heat pumps having a heat
comfort controller, this ratio may also include electrical energy
used by resistive elements to maintain a minimum air delivery
temperature (see 4.2.5).
RH(Tj)/N, the ratio of the electrical energy used for
resistive space heating during periods when the outdoor temperature
fell within the range represented by bin temperature Tj
to the total number of hours in the heating season (N), W. Except as
noted in section 4.2.5, resistive space heating is modeled as being
used to meet that portion of the building load that the heat pump
does not meet because of insufficient capacity or because the heat
pump automatically turns off at the lowest outdoor temperatures. For
heat pumps having a heat comfort controller, all or part of the
electrical energy used by resistive heaters at a particular bin
temperature may be reflected in eh(Tj)/N (see
4.2.5).
Tj, the outdoor bin temperature, [deg]F. Outdoor
temperatures are ``binned'' such that calculations are only
performed based one temperature within the bin. Bins of 5 [deg]F are
used.
nj/N, the fractional bin hours for the heating season;
the ratio of the number of hours during the heating season when the
outdoor temperature fell within the range represented by bin
temperature Tj to the total number of hours in the
heating season, dimensionless.
Obtain nj/N values from Table 19.
j, the bin number, dimensionless.
J, for each generalized climatic region, the total number of
temperature bins, dimensionless. Referring to Table 19, J is the
highest bin number (j) having a nonzero entry for the fractional bin
hours for the generalized climatic region of interest.
Fdef, the demand defrost credit described in section
3.9.2, dimensionless.
BL(Tj), the building space conditioning load
corresponding to an outdoor temperature of
Tj; the heating season building load also depends on the
generalized climatic region's outdoor design temperature and the
design heating requirement, Btu/h.
Table 19--Generalized Climatic Region Information
----------------------------------------------------------------------------------------------------------------
Region number I II III IV V VI
----------------------------------------------------------------------------------------------------------------
Heating Load Hours................ 562 909 1,363 1,701 2,202 1,974 *
Outdoor Design Temperature, TOD... 37 27 17 5 -10 30
Zero Load Temperature, TZL........ 60 58 57 55 55 58
j Tj ([deg]F)..................... Fractional Bin Hours, nj/N
-----------------------------------------------------------------------------
1 62.............................. .291 .215 .153 .132 .106 .113
2 57.............................. .239 .189 .142 .111 .092 .206
3 52.............................. .194 .163 .138 .103 .086 .215
4 47.............................. .129 .143 .137 .093 .076 .204
5 42.............................. .081 .112 .135 .100 .078 .141
6 37.............................. .041 .088 .118 .109 .087 .076
7 32.............................. .019 .056 .092 .126 .102 .034
8 27.............................. .005 .024 .047 .087 .094 .008
9 22.............................. .001 .008 .021 .055 .074 .003
10 17............................. 0 .002 .009 .036 .055 0
11 12............................. 0 0 .005 .026 .047 0
12 7.............................. 0 0 .002 .013 .038 0
13 2.............................. 0 0 .001 .006 .029 0
14 -3............................. 0 0 0 .002 .018 0
15 -8............................. 0 0 0 .001 .010 0
16 -13............................ 0 0 0 0 .005 0
17 -18............................ 0 0 0 0 .002 0
18 -23............................ 0 0 0 0 .001 0
----------------------------------------------------------------------------------------------------------------
* Pacific Coast Region.
Evaluate the building heating load using
[GRAPHIC] [TIFF OMITTED] TP09NO15.283
where,
TOD, the outdoor design temperature, [deg]F. An outdoor
design temperature is specified for each generalized climatic region
in Table 19.
DHR, the design heating requirement (see section 1.2, Definitions),
Btu/h.
Tzl, the zero load temperature, [deg]F
Calculate the design heating requirements for each generalized
climatic region as follows:
For a heat pump that delivers both cooling and heating,
[[Page 69440]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.284
where,
C = 1.3, a multiplier to provide the appropriate slope for the
heating load line, dimensionless.
Tzl, the zero load temperature, [deg]F
Qc\k=2\(95), the space cooling capacity of the unit as
determined from the A or A2 Test, whichever applies, Btu/
h.
For a heating-only heat pump,
[GRAPHIC] [TIFF OMITTED] TP09NO15.285
where,
C = 1.3, a multiplier to provide the appropriate slope for the
heating load line, dimensionless.
Tzl, the zero load temperature, [deg]F
Qh\k\(47), expressed in units of Btu/h and otherwise
defined as follows:
1. For a single-speed heating only heat pump tested as per
section 3.6.1, Qh\k\(47) = Qh(47), the space
heating capacity determined from the H1 Test.
2. For a variable-speed heating only heat pump, a section 3.6.2
single-speed heating only heat pump, or a two-capacity heating only
heat pump, Qn\k\(47) = Qn\k=2\(47), the space
heating capacity determined from the H12 Test.
For all heat pumps, HSPF accounts for the heating delivered and
the energy consumed by auxiliary resistive elements when operating
below the balance point. This condition occurs when the building
load exceeds the space heating capacity of the heat pump condenser.
For HSPF calculations for all heat pumps, see either section 4.2.1,
4.2.2, 4.2.3, or 4.2.4, whichever applies.
For heat pumps with heat comfort controllers (see section 1.2,
Definitions), HSPF also accounts for resistive heating contributed
when operating above the heat-pump-plus-comfort-controller balance
point as a result of maintaining a minimum supply temperature. For
heat pumps having a heat comfort controller, see section 4.2.5 for
the additional steps required for calculating the HSPF.
4.2.1 Additional steps for calculating the HSPF of a heat pump
having a single-speed compressor that was tested with a fixed-speed
indoor blower installed, a constant-air-volume-rate indoor blower
installed, or with no indoor blower installed.
[GRAPHIC] [TIFF OMITTED] TP09NO15.286
whichever is less; the heating mode load factor for temperature bin
j, dimensionless.
Qh(Tj), the space heating capacity of the heat
pump when operating at outdoor temperature Tj, Btu/h.
[Edot]h(Tj), the electrical power consumption
of the heat pump when operating at outdoor temperature
Tj, W.
[delta](Tj), the heat pump low temperature cut-out
factor, dimensionless.
PLFj = 1 - CD\h\ [middot] [1 -
X(Tj)], the part load factor, dimensionless.
Use Equation 4.2-2 to determine BL(Tj). Obtain
fractional bin hours for the heating season, nj/N, from
Table 19.
Determine the low temperature cut-out factor using
[GRAPHIC] [TIFF OMITTED] TP09NO15.287
[[Page 69441]]
where,
Toff, the outdoor temperature when the compressor is
automatically shut off, [deg]F. (If no such temperature exists,
Tj is always greater than Toff and
Ton).
Ton, the outdoor temperature when the compressor is
automatically turned back on, if applicable, following an automatic
shut-off, [deg]F.
Calculate Qh(Tj) and
[Edot]h(Tj) using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.288
[GRAPHIC] [TIFF OMITTED] TP09NO15.289
where,
Qh(47) and [Edot]h(47) are determined from the
H1 Test and calculated as specified in section 3.7
Qh(35) and [Edot]h(35) are determined from the
H2 Test and calculated as specified in section 3.9.1
Qh(17) and [Edot]h(17) are determined from the
H3 Test and calculated as specified in section 3.10.
4.2.2 Additional steps for calculating the HSPF of a heat pump
having a single-speed compressor and a variable-speed, variable-air-
volume-rate indoor blower. The manufacturer must provide information
about how the indoor air volume rate or the indoor blower speed
varies over the outdoor temperature range of 65 [deg]F to -23
[deg]F. Calculate the quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.290
in Equation 4.2-1 as specified in section 4.2.1 with the exception
of replacing references to the H1C Test and section 3.6.1 with the
H1C1 Test and section 3.6.2. In addition, evaluate the
space heating capacity and electrical power consumption of the heat
pump Qh(Tj) and
[Edot]h(Tj) using
[GRAPHIC] [TIFF OMITTED] TP09NO15.291
where the space heating capacity and electrical power consumption at
both low capacity
(k=1) and high capacity (k=2) at outdoor temperature Tj are
determined using
[GRAPHIC] [TIFF OMITTED] TP09NO15.292
For units where indoor blower speed is the primary control
variable, FPh\k=1\ denotes the fan speed used during the
required H11 and H31 Tests (see Table 11),
FPh\k=2\ denotes the fan speed used during the required
H12, H22, and H32 Tests, and
FPh(Tj) denotes the fan speed used by the unit
when the outdoor temperature equals Tj. For units where
indoor air volume rate is the primary control variable, the three
FPh's are similarly defined only now being expressed in
terms of air volume rates rather than fan speeds. Determine
Qh\k=1\(47) and [Edot]h\k=1\(47) from the
H11 Test, and Qh\k=2\(47) and
[Edot]h\k=2\(47) from the H12 Test. Calculate
all four quantities as specified in section 3.7. Determine
Qh\k=1\(35) and [Edot]h\k=1\(35) as specified
in section 3.6.2; determine Qh\k=2\(35) and
[Edot]h\k=2\(35) and from the H22 Test and the
calculation specified in section 3.9. Determine
Qh\k=1\(17) and [Edot]h\k=1\(17 from the
H31 Test, and Qh\k=2\(17) and
[[Page 69442]]
[Edot]h\k=2\(17) from the H32 Test. Calculate
all four quantities as specified in section 3.10.
4.2.3 Additional steps for calculating the HSPF of a heat pump
having a two-capacity compressor. The calculation of the Equation
4.2-1 quantities differ depending upon whether the heat pump would
operate at low capacity (section 4.2.3.1), cycle between low and
high capacity (Section 4.2.3.2), or operate at high capacity
(sections 4.2.3.3 and 4.2.3.4) in responding to the building load.
For heat pumps that lock out low capacity operation at low outdoor
temperatures, the manufacturer must supply information regarding the
cutoff temperature(s) so that the appropriate equations can be
selected.
[GRAPHIC] [TIFF OMITTED] TP09NO15.293
a. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at low compressor
capacity and outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TP09NO15.294
b. Evaluate the space heating capacity and electrical power
consumption (Qh\k=2\(Tj) and
[Edot]h\k=2\ (Tj)) of the heat pump when
operating at high compressor capacity and outdoor temperature Tj by
solving Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2.
Determine Qh\k=1\(62) and [Edot]h\k=1\(62)
from the H01 Test, Qh\k=1\(47) and
[Edot]h\k=1\(47) from the H11 Test, and
Qh\k=2\(47) and [Edot]h\k=2\(47) from the
H12 Test. Calculate all six quantities as specified in
section 3.7. Determine Qh\k=2\(35) and
[Edot]h\k=2\(35) from the H22 Test and, if
required as described in section 3.6.3, determine
Qh\k=1\(35) and [Edot]h\k=1\(35) from the
H21 Test. Calculate the required 35 [deg]F quantities as
specified in section 3.9. Determine Qh\k=2\(17) and
[Edot]h\k=2\(17) from the H32 Test and, if
required as described in section 3.6.3, determine
Qh\k=1\(17) and [Edot]h\k=1\(17) from the
H31 Test. Calculate the required 17 [deg]F quantities as
specified in section 3.10.
4.2.3.1 Steady-state space heating capacity when operating at
low compressor capacity is greater than or equal to the building
heating load at temperature Tj,
Qh\k=1\(Tj) >=BL(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.295
Where,
X\k=1\(Tj) = BL(Tj)/
Qh\k=1\(Tj), the heating mode low capacity
load factor for temperature bin j, dimensionless.
PLFj = 1 - CD\h\ [middot] [ 1 -
X\k=1\(Tj) ], the part load factor, dimensionless.
[delta]'(Tj), the low temperature cutoff factor,
dimensionless.
Determine the low temperature cut-out factor using
[GRAPHIC] [TIFF OMITTED] TP09NO15.296
Where,
Toff and Ton are defined in section 4.2.1. Use
the calculations given in section 4.2.3.3, and not the above, if:
(a) The heat pump locks out low capacity operation at low outdoor
temperatures and
(b) Tj is below this lockout threshold temperature.
4.2.3.2 Heat pump alternates between high (k=2) and low (k=1)
compressor capacity to satisfy the building heating load at a
temperature Tj, Qh\k=1\(Tj) <
BL(Tj) < Qh\k=2\(Tj).
[[Page 69443]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.297
Where,
[GRAPHIC] [TIFF OMITTED] TP09NO15.298
X\k=2\(Tj) = 1 - X\k=1\(Tj) the heating mode,
high capacity load factor for temperature bin j,
dimensionless.
Determine the low temperature cut-out factor,
[delta]'(Tj), using Equation 4.2.3-3.
4.2.3.3 Heat pump only operates at high (k=2) compressor
capacity at temperature Tj and its capacity is greater
than the building heating load, BL(Tj) <
Qh\k=2\(Tj). This section applies to units
that lock out low compressor capacity operation at low outdoor
temperatures.
[GRAPHIC] [TIFF OMITTED] TP09NO15.299
Where,
X\k=2\(Tj)= BL(Tj)/
Qh\k=2\(Tj).
PLFj = 1 - Ch(k = 2) * [1 - X\k=2\(Tj)]
Determine the low temperature cut-out factor,
[delta](Tj), using Equation 4.2.3-3.
4.2.3.4 Heat pump must operate continuously at high (k=2)
compressor capacity at temperature Tj, BL(Tj)
>= Qh\k=2\(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.400
4.2.4 Additional steps for calculating the HSPF of a heat pump
having a variable-speed compressor. Calculate HSPF using Equation
4.2-1. Evaluate the space heating capacity,
Qh\k=1\(Tj), and electrical power consumption,
[Edot]h\k=1\(Tj), of the heat pump when
operating at minimum compressor speed and outdoor temperature
Tj using
[GRAPHIC] [TIFF OMITTED] TP09NO15.401
Where,
Qh\k=1\(62) and [Edot]h\k=1\(62) are
determined from the H01 Test
Qh\k=1\(47) and [Edot]h\k=1\(47) are
determined from the H11Test,
and all four quantities are calculated as specified in section 3.7.
[[Page 69444]]
Evaluate the space heating capacity,
Qh\k=2\(Tj), and electrical power consumption,
[Edot]h\k=2\(Tj), of the heat pump when
operating at maximum compressor speed and outdoor temperature
Tj by solving Equations 4.2.2-3 and 4.2.2-4,
respectively, for k=2. Determine the Equation 4.2.2-3 and 4.2.2-4
quantities Qh\k=2\(47) and [Edot]h\k=2\(47)
from the H12 Test and the calculations specified in
section 3.7. Determine Qh\k=2\(35) and
[Edot]h\k=2\(35) from the H22 Test and the
calculations specified in section 3.9 or, if the H22 Test
is not conducted, by conducting the calculations specified in
section 3.6.4. Determine Qh\k=2\(17) and
[Edot]h\k=2\(17) from the H32 Test and the
calculations specified in section 3.10. If H42 test is
conducted, evaluate the space heating capacity,
Qh\k=2\(Tj), and electrical power consumption,
[Edot]h\k=2\(Tj), of the heat pump when
operating at maximum compressor speed and outdoor temperature
Tj by using the following equation instead of Equations
4.2.2-3 and 4.2.2-4. Determine the quantities
Qh\k=2\(Tl) and
[Edot]h\k=2\(Tl) from the H42 Test
and the calculations specified in section 3.7.
[GRAPHIC] [TIFF OMITTED] TP09NO15.402
Where Tl is the outdoor temperature where the H42 test is
conducted.
Calculate the space heating capacity,
Qh\k=v\(Tj), and electrical power consumption,
[Edot]h\k=v\(Tj), of the heat pump when
operating at outdoor temperature Tj and the intermediate
compressor speed used during the section 3.6.4 H2V Test
using
[GRAPHIC] [TIFF OMITTED] TP09NO15.403
Where,
Qh\k=v\(35) and [Edot]h\k=v\(35) are
determined from the H2V Test and calculated as specified
in section 3.9. Approximate the slopes of the k=v intermediate speed
heating capacity and electrical power input curves, MQ
and ME, as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.404
Use Equations 4.2.4-1 and 4.2.4-2, respectively, to calculate
Qh\k=1\(35) and [Edot]h\k=1\(35). The
calculation of Equation 4.2-1 quantities
eh(Tj)/N and RH(Tj)/N differs
depending upon whether the heat pump would operate at minimum speed
(section 4.2.4.1), operate at an intermediate speed (section
4.2.4.2), or operate at maximum speed (section 4.2.4.3) in
responding to the building load.
[[Page 69445]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.405
and [delta](Tj) is evaluated using Equation 4.2.3-3
while,
Qh\k=i\(Tj) = BL(Tj), the space
heating capacity delivered by the unit in matching the building load
at temperature (Tj), Btu/h. The matching occurs with the
heat pump operating at compressor speed k=i.
COP\k=i\(Tj), the steady-state coefficient of performance
of the heat pump when operating at compressor speed k=i and
temperature Tj, dimensionless.
For each temperature bin where the heat pump operates at an
intermediate compressor speed, determine COP\k=i\(Tj)
using,
COP\k=i\(Tj) = A + B [middot] Tj + C [middot]
Tj\2\.
For each heat pump, determine the coefficients A, B, and C by
conducting the following calculations once:
[GRAPHIC] [TIFF OMITTED] TP09NO15.406
Where,
T3, the outdoor temperature at which the heat pump, when
operating at minimum compressor speed, provides a space heating
capacity that is equal to the building load
(Qh\k=1\(T3) = BL(T3)), [deg]F.
Determine T3 by equating Equations 4.2.4-1 and 4.2-2 and
solving for outdoor temperature:
[GRAPHIC] [TIFF OMITTED] TP09NO15.407
Tvh, the outdoor temperature at which the heat pump, when
operating at the intermediate compressor speed used during the
section 3.6.4 H2V Test, provides a space heating capacity
that is equal to the building load
(Qh\k=v\(Tvh) = BL(Tvh)), [deg]F.
Determine Tvh by equating Equations 4.2.4-3 and 4.2-2 and
solving for outdoor temperature.
T4, the outdoor temperature at which the heat pump, when
operating at maximum compressor speed, provides a space heating
capacity that is equal to the building load
(Qh\k=2\(T4) = BL(T4)), [deg]F.
[[Page 69446]]
Determine T4 by equating Equations 4.2.2-3 (k=2) and 4.2-
2 and solving for outdoor temperature.
[GRAPHIC] [TIFF OMITTED] TP09NO15.408
[GRAPHIC] [TIFF OMITTED] TP09NO15.409
For multiple-split heat pumps (only), the following procedures
supersede the above requirements for calculating
COPh\k=i\(Tj). For each temperature bin where
T3 >Tj >Tvh,
[GRAPHIC] [TIFF OMITTED] TP09NO15.410
4.2.4.3 Heat pump must operate continuously at maximum (k=2)
compressor speed at temperature Tj, BL(Tj)
>=Qh\k=2\(Tj). Evaluate the Equation 4.2-1
quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.411
as specified in section 4.2.3.4 with the understanding that
Qh\k=2\(Tj) and
[Edot]h\k=2\(Tj) correspond to maximum
compressor speed operation and are derived from the results of the
specified section 3.6.4 tests. If H42 test is conducted
in place of H12, evaluate
Qh\k=2\(Tj) and
[Edot]h\k=2\(Tj) using the following equation
instead of equations 4.2.2-3 and 4.2.2-4.
[GRAPHIC] [TIFF OMITTED] TP09NO15.412
Where, TL is the ambient dry bulb temperature where
H42 test is conducted.
4.2.5 Heat pumps having a heat comfort controller. Heat pumps
having heat comfort controllers, when set to maintain a typical
minimum air delivery temperature, will cause the heat pump condenser
to operate less because of a greater contribution from the resistive
elements. With a conventional heat pump, resistive heating is only
initiated if the heat pump condenser cannot meet the building load
(i.e., is delayed until a second stage call from the indoor
thermostat). With a heat comfort controller, resistive heating can
occur even though the heat pump condenser has adequate capacity to
meet the building load (i.e., both on during a first stage call from
the indoor thermostat). As a result, the outdoor temperature where
the heat pump compressor no longer cycles (i.e., starts to run
continuously), will be lower than if
[[Page 69447]]
the heat pump did not have the heat comfort controller.
4.2.5.1 Heat pump having a heat comfort controller: additional
steps for calculating the HSPF of a heat pump having a single-speed
compressor that was tested with a fixed-speed indoor blower
installed, a constant-air-volume-rate indoor blower installed, or
with no indoor blower installed. Calculate the space heating
capacity and electrical power of the heat pump without the heat
comfort controller being active as specified in section 4.2.1
(Equations 4.2.1-4 and 4.2.1-5) for each outdoor bin temperature,
Tj, that is listed in Table 19. Denote these capacities
and electrical powers by using the subscript ``hp'' instead of
``h.'' Calculate the mass flow rate (expressed in pounds-mass of dry
air per hour) and the specific heat of the indoor air (expressed in
Btu/lbmda [middot] [deg]F) from the results of the H1
Test using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.413
Where Vis, Vimx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 19, calculate
the nominal temperature of the air leaving the heat pump condenser
coil using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.414
Evaluate eh(Tj/N), RH(Tj)/N,
X(Tj), PLFj, and [delta](Tj) as
specified in section 4.2.1. For each bin calculation, use the space
heating capacity and electrical power from Case 1 or Case 2,
whichever applies.
Case 1. For outdoor bin temperatures where
To(Tj) is equal to or greater than
TCC (the maximum supply temperature determined according
to section 3.1.9), determine Qh(Tj) and
[Edot]h(Tj) as specified in section 4.2.1
(i.e., Qh(Tj) = Qhp(Tj)
and [Edot]hp(Tj) =
[Edot]hp(Tj)). Note: Even though
To(Tj) >=Tcc, resistive heating may
be required; evaluate Equation 4.2.1-2 for all bins.
Case 2. For outdoor bin temperatures where
To(Tj) >Tcc, determine
Qh(Tj) and [Edot]h(Tj)
using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.415
NOTE: Even though To(Tj) cc,
additional resistive heating may be required; evaluate Equation
4.2.1-2 for all bins.
4.2.5.2 Heat pump having a heat comfort controller: Additional
steps for calculating the HSPF of a heat pump having a single-speed
compressor and a variable-speed, variable-air-volume-rate indoor
blower. Calculate the space heating capacity and electrical power of
the heat pump without the heat comfort controller being active as
specified in section 4.2.2 (Equations 4.2.2-1 and 4.2.2-2) for each
outdoor bin temperature, Tj, that is listed in Table 19.
Denote these capacities and electrical powers by using the subscript
``hp'' instead of ``h.'' Calculate the mass flow rate (expressed in
pounds-mass of dry air per hour) and the specific heat of the indoor
air (expressed in Btu/lbmda [middot] [deg]F) from the
results of the H12 Test using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.416
Cp,da = 0.24 + 0.444 * Qn
Where ViS, Vimx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 19, calculate
the nominal temperature of the air leaving the heat pump condenser
coil using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.417
Evaluate eh(Tj)/N, RH(Tj)/N,
X(Tj), PLFj, and [delta](Tj) as
specified in section 4.2.1 with the exception of replacing
references to the H1C Test and section 3.6.1 with the
H1C1 Test and section 3.6.2. For each bin calculation,
use the space heating capacity and electrical power from Case 1 or
Case 2, whichever applies.
Case 1. For outdoor bin temperatures where
To(Tj) is equal to or greater than
TCC (the maximum supply temperature determined according
to section 3.1.9), determine Qh(Tj) and
[Edot]h(Tj) as specified in section 4.2.2
(i.e. Qh(Tj) = Qhp(Tj)
and [Edot]h(Tj) =
[Edot]hp(Tj)). Note: Even though
To(Tj) >=TCC, resistive heating may
be required; evaluate Equation 4.2.1-2 for all bins.
Case 2. For outdoor bin temperatures where
To(Tj) CC, determine
Qh(Tj) and [Edot]h(Tj)
using,
[[Page 69448]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.418
Note: Even though To(Tj) cc,
additional resistive heating may be required; evaluate Equation
4.2.1-2 for all bins.
4.2.5.3 Heat pumps having a heat comfort controller: additional
steps for calculating the HSPF of a heat pump having a two-capacity
compressor. Calculate the space heating capacity and electrical
power of the heat pump without the heat comfort controller being
active as specified in section 4.2.3 for both high and low capacity
and at each outdoor bin temperature, Tj, that is listed
in Table 19. DeNote these capacities and electrical powers by using
the subscript ``hp'' instead of ``h.'' For the low capacity case,
calculate the mass flow rate (expressed in pounds-mass of dry air
per hour) and the specific heat of the indoor air (expressed in Btu/
lbmda [middot] [deg]F) from the results of the
H11 Test using:
[GRAPHIC] [TIFF OMITTED] TP09NO15.419
Where Vis, Vimx, v'n (or
vn), and Wn are defined following Equation 3-
1. For each outdoor bin temperature listed in Table 19, calculate
the nominal temperature of the air leaving the heat pump condenser
coil when operating at low capacity using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.420
Repeat the above calculations to determine the mass flow rate
(mda\k=2\) and the specific heat of the indoor air
(Cp,da\k=2\) when operating at high capacity by using the
results of the H12 Test. For each outdoor bin temperature
listed in Table 19, calculate the nominal temperature of the air
leaving the heat pump condenser coil when operating at high capacity
using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.421
Evaluate eh(Tj)/N, RH(Tj)/N,
X\k=1\(Tj), and/or X\k=2\(Tj),
PLFj, and [delta]'(Tj) or
[delta]''(Tj) as specified in section 4.2.3.1. 4.2.3.2,
4.2.3.3, or 4.2.3.4, whichever applies, for each temperature bin. To
evaluate these quantities, use the low-capacity space heating
capacity and the low-capacity electrical power from Case 1 or Case
2, whichever applies; use the high-capacity space heating capacity
and the high-capacity electrical power from Case 3 or Case 4,
whichever applies.
Case 1. For outdoor bin temperatures where
To\k=1\(Tj) is equal to or greater than
TCC (the maximum supply temperature determined according
to section 3.1.9), determine Qh\k=1\(Tj) and
[Edot]h\k=1\(Tj) as specified in section 4.2.3
(i.e., Qh\k=1\(Tj) =
Qhp\k=1\(Tj) and
[Edot]h\k=1\(Tj) =
[Edot]hp\k=1\(Tj).
Note: Even though To\k=1\(Tj)
>=TCC, resistive heating may be required; evaluate
RH(Tj)/N for all bins.
Case 2. For outdoor bin temperatures where
To\k=1\(Tj) CC, determine
Qh\k=1\(Tj) and
[Edot]h\k=1\(Tj) using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.422
Note: Even though To\k=1\(Tj)
>=Tcc, additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
Case 3. For outdoor bin temperatures where
To\k=2\(Tj) is equal to or greater than
TCC, determine Qh\k=2\(Tj) and
[Edot]h\k=2\(Tj) as specified in section 4.2.3
(i.e., Qh\k=2\(Tj) =
Qhp\k=2\(Tj) and
[Edot]h\k=2\(Tj) =
[Edot]hp\k=2\(Tj)).
Note: Even though To\k=2\(Tj)
CC, resistive heating may be required; evaluate
RH(Tj)/N for all bins.
Case 4. For outdoor bin temperatures where
To\k=2\(Tj) CC, determine
Qh\k=2\(Tj) and
[Edot]h\k=2\(Tj) using,
[[Page 69449]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.423
Note: Even though To\k=2\(Tj)
cc, additional resistive heating may be required;
evaluate RH(Tj)/N for all bins.
4.2.5.4 Heat pumps having a heat comfort controller: additional
steps for calculating the HSPF of a heat pump having a variable-
speed compressor. [Reserved]
4.2.6 Additional steps for calculating the HSPF of a heat pump
having a triple-capacity compressor. The only triple-capacity heat
pumps covered are triple-capacity, northern heat pumps.
For such heat pumps, the calculation of the Eq. 4.2-1 quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.424
differ depending on whether the heat pump would cycle on and off at
low capacity (section 4.2.6.1), cycle on and off at high capacity
(section 4.2.6.2), cycle on and off at booster capacity (4.2.6.3),
cycle between low and high capacity (section 4.2.6.4), cycle between
high and booster capacity (section 4.2.6.5), operate continuously at
low capacity (4.2.6.6), operate continuously at high capacity
(section 4.2.6.7), operate continuously at booster capacity
(4.2.6.8), or heat solely using resistive heating (also section
4.2.6.8) in responding to the building load. As applicable, the
manufacturer must supply information regarding the outdoor
temperature range at which each stage of compressor capacity is
active. As an informative example, data may be submitted in this
manner: At the low (k=1) compressor capacity, the outdoor
temperature range of operation is 40 [deg]F <= T <= 65 [deg]F; At
the high (k=2) compressor capacity, the outdoor temperature range of
operation is 20 [deg]F <= T <= 50 [deg]F; At the booster (k=3)
compressor capacity, the outdoor temperature range of operation is -
20 [deg]F <= T <= 30[emsp14][deg]F.
a. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at low compressor
capacity and outdoor temperature Tj using the equations given in
section 4.2.3 for Qh\k=1\(Tj) and
[Edot]h\k=1\ (Tj)) In evaluating the section
4.2.3 equations, Determine Qh\k=1\(62) and
[Edot]h\k=1\(62) from the H01 Test,
Qh\k=1\(47) and [Edot]h\k=1\(47) from the
H11 Test, and Qh\k=2\(47) and
[Edot]h\k=2\(47) from the H12 Test. Calculate
all four quantities as specified in section 3.7. If, in accordance
with section 3.6.6, the H31 Test is conducted, calculate
Qh\k=1\(17) and [Edot]h\k=1\(17) as specified
in section 3.10 and determine Qh\k=1\(35) and
[Edot]h\k=1\(35) as specified in section 3.6.6.
b. Evaluate the space heating capacity and electrical power
consumption (Qh\k=2\(Tj) and
[Edot]h\k=2\ (Tj)) of the heat pump when
operating at high compressor capacity and outdoor temperature Tj by
solving Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2.
Determine Qh\k=1\(62) and [Edot]h\k=1\(62)
from the H01 Test, Qh\k=1\(47) and
[Edot]h\k=1\(47) from the H11 Test, and
Qh\k=2\(47) and [Edot]h\k=2\(47) from the
H12 Test, evaluated as specified in section 3.7.
Determine the equation input for Qh\k=2\(35) and
[Edot]h\k=2\(35) from the H22, evaluated as
specified in section 3.9.1. Also, determine Qh\k=2\(17)
and [Edot]h\k=2\(17) from the H32 Test,
evaluated as specified in section 3.10.
c. Evaluate the space heating capacity and electrical power
consumption of the heat pump when operating at booster compressor
capacity and outdoor temperature Tj using
[GRAPHIC] [TIFF OMITTED] TP09NO15.426
Determine Qh\k=3\(17) and [Edot]h\k=3\(17)
from the H33 Test and determine Qh\k=2\(2) and
[Edot]h\k=3\(2) from the H43 Test. Calculate
all four quantities as specified in section 3.10. Determine the
equation input for Qh\k=3\(35) and
[Edot]h\k=3\(35) as specified in section 3.6.6.
4.2.6.1 Steady-state space heating capacity when operating at
low compressor capacity is greater than or equal to the building
heating load at temperature Tj,
Qh\k=1\(Tj) >=BL(Tj)., and the heat
pump permits low compressor capacity at Tj. Evaluate the
quantities
[[Page 69450]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.427
using Eqs. 4.2.3-1 and 4.2.3-2, respectively. Determine the equation
inputs X\k=1\(Tj), PLFj, and
[delta]'(Tj) as specified in section 4.2.3.1. In
calculating the part load factor, PLFj, use the low-
capacity cyclic-degradation coefficient CD\h\, [or
equivalently, CD\h\(k=1)] determined in accordance with
section 3.6.6.
4.2.6.2 Heat pump only operates at high (k=2) compressor
capacity at temperature Tj and its capacity is greater
than or equal to the building heating load, BL(Tj)
h\k=2\(Tj). Evaluate the quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.428
as specified in section 4.2.3.3. Determine the equation inputs
X\k=2\(Tj), PLFj, and [delta]'(Tj)
as specified in section 4.2.3.3. In calculating the part load
factor, PLFj, use the high-capacity cyclic-degradation
coefficient, CD\h\(k=2) determined in accordance with
section 3.6.6.
4.2.6.3 Heat pump only operates at high (k=3) compressor
capacity at temperature Tj and its capacity is greater
than or equal to the building heating load, BL(Tj)
<=Qh\k=3\(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.429
where
Xk\=3\(Tj) = BL(Tj)/Qhk\=3\(Tj) and PLFj = 1 - C5h (k = 3) * [1
- Xk\=3\(Tj)
Determine the low temperature cut-out factor,
[delta]'(Tj), using Eq. 4.2.3-3. Use the booster-capacity
cyclic-degradation coefficient, CD\h\(k=3) determined in
accordance with section 3.6.6.
4.2.6.4 Heat pump alternates between high (k=2) and low (k=1)
compressor capacity to satisfy the building heating load at a
temperature Tj, Qh\k=1\(Tj)
j) h\k=2\(Tj). Evaluate the
quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.430
as specified in section 4.2.3.2. Determine the equation inputs
X\k=1\(Tj), X\k=2\(Tj), and
[delta]'(Tj) as specified in section 4.2.3.2.
4.2.6.5 Heat pump alternates between high (k=2) and booster
(k=3) compressor capacity to satisfy the building heating load at a
temperature Tj, Qh\k=2\(Tj)
j) h\k=3\(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.431
and X\k=3\(Tj) = X\k=2\(Tj) = the heating
mode, booster capacity load factor for temperature bin j,
dimensionless. Determine the low temperature cut-out factor,
[delta]'(Tj), using Eq. 4.2.3-3.
4.2.6.6 Heat pump only operates at low (k=1) capacity at
temperature Tj and its capacity is less than the building
heating load, BL(Tj) > Qh\k=1\(Tj).
[GRAPHIC] [TIFF OMITTED] TP09NO15.432
[[Page 69451]]
Where the low temperature cut-out factor, [delta]'(Tj), is
calculated using Eq. 4.2.3-3.
4.2.6.7 Heat pump only operates at high (k = 2) capacity at
temperature Tj and its capacity is less than the building heating
load, BL(Tj) > Qh\k=2\(Tj). Evaluate the
quantities
[GRAPHIC] [TIFF OMITTED] TP09NO15.433
as specified in section 4.2.3.4. Calculate [delta]''(Tj) using the
equation given in section 4.2.3.4.
4.2.6.8 Heat pump only operates at booster (k = 3) capacity at
temperature Tj and its capacity is less than the building heating
load, BL(Tj) > Qh\k=3\(Tj). or the
system converts to using only resistive heating.
[GRAPHIC] [TIFF OMITTED] TP09NO15.434
Where [delta]''(Tj) is calculated as specified in section 4.2.3.4 if
the heat pump is operating at its booster compressor capacity. If
the heat pump system converts to using only resistive heating at
outdoor temperature Tj, set [delta]'(Tj) equal
to zero.
4.2.7 Additional steps for calculating the HSPF of a heat pump
having a single indoor unit with multiple blowers. The calculation
of the Eq. 4.2-1 quantities eh(Tj)/N and
RH(Tj)/N are evaluated as specified in applicable below
subsection.
4.2.7.1 For multiple blower heat pumps that are connected to a
singular, single-speed outdoor unit.
a. Calculate the space heating capacity, Qhk\=1\(Tj), and
electrical power consumption, [Edot]hk\=1\(Tj), of the heat pump
when operating at the heating minimum air volume rate and outdoor
temperature Tj using Eqs. 4.2.2-3 and 4.2.2-4,
respectively. Use these same equations to calculate the space
heating capacity, Qhk\=2\ (Tj) and electrical power consumption,
[Edot]hk\=2\(Tj), of the test unit when operating at the heating
full-load air volume rate and outdoor temperature Tj. In
evaluating Eqs. 4.2.2-3 and 4.2.2-4, determine the quantities
Qhk\=1\ (47) and [Edot]hk\=1\(47) from the H11 Test;
determine Qhk\=2\ (47) and [Edot]hk\=2\(47) from the H12
Test. Evaluate all four quantities according to section 3.7.
Determine the quantities Qhk\=1\(35) and [Edot]hk\=1\(35) as
specified in section 3.6.2. Determine Qhk\=2\(35) and
[Edot]hk\=2\(35) from the H22 Frost Accumulation Test as
calculated according to section 3.9.1. Determine the quantities
Qhk\=1\(17) and [Edot]hk\=1\(17) from the H31 Test, and
Qhk\=2\(17) and [Edot]hk\=2\(17) from the H32 Test.
Evaluate all four quantities according to section 3.10. Refer to
section 3.6.2 and Table 11 for additional information on the
referenced laboratory tests.
b. Determine the heating mode cyclic degradation coefficient,
CDh, as per sections 3.6.2 and 3.8 to 3.8.1. Assign this
same value to CDh(k = 2).
c. Except for using the above values of Qhk\=1\(Tj),
[Edot]hk\=1\(Tj), Qhk\=2\(Tj), Eihk\=2\(Tj), CDh, and
CDh(k = 2), calculate the quantities
eh(Tj)/N as specified in section 4.2.3.1 for
cases where Qhk\=1\(Tj) >= BL(Tj). For all other outdoor
bin temperatures, Tj, calculate eh(Tj)/N and
RHh(Tj)/N as specified in section 4.2.3.3 if Qhk\=2\(Tj)
> BL(Tj) or as specified in section 4.2.3.4 if Qhk\=2\(Tj) <=
BL(Tj).
4.2.7.2 For multiple blower heat pumps connected to either a
lone outdoor unit with a two-capacity compressor or to two separate
but identical model single-speed outdoor units. Calculate the
quantities eh(Tj)/N and RH(Tj)/N as
specified in section 4.2.3.
4.3 Calculations of Off-mode Seasonal Power and Energy
Consumption.
4.3.1 For central air conditioners and heat pumps with a cooling
capacity of:
less than 36,000 Btu/h, determine the off mode rating, PW,OFF,
with the following equation:
[GRAPHIC] [TIFF OMITTED] TP09NO15.435
4.3.2 Calculate the off mode energy consumption for both central
air conditioner and heat pumps for the shoulder season, E1, using:
E1 = P1 [middot] SSH; and the off mode energy consumption of a CAC,
only, for the heating season, E2, using: E2 = P2 [middot] HSH; where
P1 and P2 is determined in Section 3.13. HSH can be determined by
multiplying the heating season-hours from Table 20 with the
fractional Bin-hours, from Table 19, that pertain to the range of
temperatures at which the crankcase heater operates. If the
crankcase heater is controlled to disable for the heating season,
the temperature range at which the crankcase heater operates is
defined to be from 72 [deg]F to five degrees Fahrenheit below a
turn-off temperature specified by the manufacturer in the DOE
Compliance Certification Database. If the crankcase heater is
operated during the heating season, the temperature range at which
the crankcase heater operates is defined to be from 72 [deg]F to -23
[deg]F, the latter of which is a temperature that sets the range of
Bin-hours to encompass all outside air temperatures in the heating
season.
SSH can be determined by multiplying the shoulder season-hours
from Table 20 with the fractional Bin-hours in Table 21.
Table 20--Representative Cooling and Heating Load Hours and the Corresponding Set of Seasonal Hours for Each
Generalized Climatic Region
----------------------------------------------------------------------------------------------------------------
Cooling Heating Shoulder
Climatic region Cooling load Heating load season hours season hours season hours
hours CLHR hours HLHR CSHR HSHR SSHR
----------------------------------------------------------------------------------------------------------------
I............................... 2,400 750 6,731 1,826 203
II.............................. 1,800 1,250 5,048 3,148 564
III............................. 1,200 1,750 3,365 4,453 942
IV.............................. 800 2,250 2,244 5,643 873
Rating Values................... 1,000 2,080 2,805 5,216 739
V............................... 400 2,750 1,122 6,956 682
[[Page 69452]]
VI.............................. 200 2,750 561 6,258 1,941
----------------------------------------------------------------------------------------------------------------
[GRAPHIC] [TIFF OMITTED] TP09NO15.436
Region I: HSH = 2.4348HLH;
Region II: HSH = 2.5182HLH;
Region III: HSH = 2.5444HLH;
Region IV: HSH = 2.5078HLH;
Region V: HSH = 2.5295HLH;
Region VI: HSH = 2.2757HLH;
SSH is evaluated: SSH = 8760 - (CSH + HSH). where CSH = the
cooling season hours calculated using CSH = 2.8045 [middot] CLH.
Table 21--Fractional Bin Hours for the Shoulder Season Hours for All
Regions
------------------------------------------------------------------------
Fractional bin hours
Tj([deg]F) ------------------------------------
Air conditioners Heat pumps
------------------------------------------------------------------------
72................................. 0.333 0.167
67................................. 0.667 0.333
62................................. 0 0.333
57................................. 0 0.167
------------------------------------------------------------------------
[GRAPHIC] [TIFF OMITTED] TP09NO15.437
4.3.4 For air conditioners, the annual off mode energy
consumption, ETOTAL, is: ETOTAL = E1 + E2.
4.3.5 For heat pumps, the annual off mode energy consumption,
ETOTAL, is E1.
4.4 Calculations of the Actual and Representative Regional
Annual Performance Factors for Heat Pumps.
4.4.1 Calculation of actual regional annual performance factors
(APFA) for a particular location and for each
standardized design heating requirement.
[GRAPHIC] [TIFF OMITTED] TP09NO15.438
Where,
CLHA = the actual cooling hours for a particular location
as determined using the map given in Figure 2, hr.
Qc\k\(95) = the space cooling capacity of the unit as
determined from the A or A2 Test, whichever applies, Btu/
h.
HLHA = the actual heating hours for a particular location
as determined using the map given in Figure 1, hr.
DHR = the design heating requirement used in determining the HSPF;
refer to section 4.2 and see section 1.2, Definitions, Btu/h.
C = defined in section 4.2 following Equation 4.2-2, dimensionless.
SEER = the seasonal energy efficiency ratio calculated as specified
in section 4.1, Btu/W[middot]h.
HSPF = the heating seasonal performance factor calculated as
specified in section
[[Page 69453]]
4.2 for the generalized climatic region that includes the particular
location of interest (see Figure 1), Btu/W[middot]h. The HSPF should
correspond to the actual design heating requirement (DHR), if known.
If it does not, it may correspond to one of the standardized design
heating requirements referenced in section 4.2.
P1 is the shoulder season per-compressor off mode power, as
determined in section 3.13, W.
SSH is the shoulder season hours, hr.
P2 is the heating season per-compressor off mode power, as
determined in section 3.13, W.
HSH is the heating season hours, hr.
4.4.2 Calculation of representative regional annual performance
factors (APFR) for each generalized climatic region and
for each standardized design heating requirement.
[GRAPHIC] [TIFF OMITTED] TP09NO15.439
Where,
CLHR = the representative cooling hours for each
generalized climatic region, Table 22, hr.
HLHR = the representative heating hours for each
generalized climatic region, Table 22, hr.
HSPF = the heating seasonal performance factor calculated as
specified in section 4.2 for the each generalized climatic region
and for each standardized design heating requirement within each
region, Btu/W.h.
The SEER, Qc\k\(95), DHR, and C are the same
quantities as defined in section 4.4.1. Figure 1 shows the
generalized climatic regions.
Table 22--Representative Cooling and Heating Load Hours for Each
Generalized Climatic Region
------------------------------------------------------------------------
Region CLHR HLHR
------------------------------------------------------------------------
I....................................... 2400 750
II...................................... 1800 1250
III..................................... 1200 1750
IV...................................... 800 2250
V....................................... 400 2750
VI...................................... 200 2750
------------------------------------------------------------------------
4.5. Rounding of SEER, HSPF, and APF for reporting purposes.
After calculating SEER according to section 4.1, HSPF according to
section 4.2, and APF according to section 4.4, round the values off
as specified in subpart B 430.23(m) of Title 10 of the Code of
Federal Regulations.
[[Page 69454]]
[GRAPHIC] [TIFF OMITTED] TP09NO15.440
4.6 Calculations of the SHR, which should be computed for
different equipment configurations and test conditions specified in
Table 23.
[[Page 69455]]
Table 23 Applicable Test Conditions For Calculation of the Sensible Heat Ratio
----------------------------------------------------------------------------------------------------------------
Reference
Equipment configuration Table No. of SHR computation with Computed values
Appendix M results from
----------------------------------------------------------------------------------------------------------------
Units Having a Single-Speed 4 B Test................. SHR(B).
Compressor and a Fixed-Speed Indoor
blower, a Constant Air Volume Rate
Indoor blower, or No Indoor blower.
Units Having a Single-Speed 5 B2 and B1 Tests........ SHR(B1), SHR(B2).
Compressor That Meet the Section
3.2.2.1 Indoor Unit Requirements.
Units Having a Two-Capacity 6 B2 and B1 Tests........ SHR(B1), SHR(B2).
Compressor.
Units Having a Variable-Speed 7 B2 and B1 Tests........ SHR(B1), SHR(B2).
Compressor.
----------------------------------------------------------------------------------------------------------------
The SHR is defined and calculated as follows:
[GRAPHIC] [TIFF OMITTED] TP09NO15.441
Where both the total and sensible cooling capacities are determined
from the same cooling mode test and calculated from data collected
over the same 30-minute data collection interval.
4.7 Calculations of the Energy Efficiency Ratio (EER). Calculate
the energy efficiency ratio using,
[GRAPHIC] [TIFF OMITTED] TP09NO15.442
Where Qc\k\(T) and [Edot]c\k\(T) are the
space cooling capacity and electrical power consumption determined
from the 30-minute data collection interval of the same steady-state
wet coil cooling mode test and calculated as specified in section
3.3. Add the letter identification for each steady-state test as a
subscript (e.g., EERA2) to differentiate among the
resulting EER values.
0
12. Section 430.32 is amended by revising paragraph (c) to read as
follows:
Sec. 430.32 Energy and water conservation standards and their
compliance dates.
* * * * *
(c) Central air conditioners and heat pumps. The energy
conservation standards defined in terms of the heating seasonal
performance factor are based on Region IV, the minimum standardized
design heating requirement, and the provisions of 10 CFR 429.16 of this
chapter.
(1) Each basic model of single-package central air conditioners and
central air conditioning heat pumps and each individual combination of
split-system central air conditioners and central air conditioning heat
pumps manufactured on or after January 1, 2015, shall have a Seasonal
Energy Efficiency Ratio and Heating Seasonal Performance Factor not
less than:
------------------------------------------------------------------------
Seasonal Heating
energy seasonal
Product class efficiency performance
ratio (SEER) factor (HSPF)
------------------------------------------------------------------------
(i) Split-system air conditioners....... 13 ..............
(ii) Split-system heat pumps............ 14 8.2
(iii) Single-package air conditioners... 14 ..............
(iv) Single-package heat pumps.......... 14 8.0
(v) Small-duct, high-velocity systems... 12 7.2
(vi)(A) Space-constrained products--air 12 ..............
conditioners...........................
(vi)(B) Space-constrained products--heat 12 7.4
pumps..................................
------------------------------------------------------------------------
(2) In addition to meeting the applicable requirements in paragraph
(c)(2) of this section, products in product class (i) of that paragraph
(i.e., split-system air conditioners) that are installed on or after
January 1, 2015, and
[[Page 69456]]
installed in the States of Alabama, Arkansas, Delaware, Florida,
Georgia, Hawaii, Kentucky, Louisiana, Maryland, Mississippi, North
Carolina, Oklahoma, South Carolina, Tennessee, Texas, or Virginia, or
in the District of Columbia, shall have a Seasonal Energy Efficiency
Ratio not less than 14. The least efficient combination of each basic
model must comply with this standard.
(3) In addition to meeting the applicable requirements in
paragraphs (c)(2) of this section, products in product classes (i) and
(iii) of paragraph (c)(2) (i.e., split-system air conditioners and
single-package air conditioners) that are installed on or after January
1, 2015, and installed in the States of Arizona, California, Nevada, or
New Mexico shall have a Seasonal Energy Efficiency Ratio not less than
14 and have an Energy Efficiency Ratio (at a standard rating of
95[emsp14][deg]F dry bulb outdoor temperature) not less than the
following:
------------------------------------------------------------------------
Energy
Product class efficiency
ratio (EER)
------------------------------------------------------------------------
(i) Split-system rated cooling capacity less than 45,000 12.2
Btu/hr.................................................
(ii) Split-system rated cooling capacity equal to or 11.7
greater than 45,000 Btu/hr.............................
(iii) Single-package systems............................ 11.0
------------------------------------------------------------------------
The least efficient combination of each basic model must comply
with this standard.
(4) Each basic model of single-package central air conditioners and
central air conditioning heat pumps and each individual combination of
split-system central air conditioners and central air conditioning heat
pumps manufactured on or after January 1, 2015, shall have an average
off mode electrical power consumption not more than the following:
------------------------------------------------------------------------
Average off
mode power
Product class consumption
PW,OFF
(watts)
------------------------------------------------------------------------
(i) Split-system air conditioners....................... 30
(ii) Split-system heat pumps............................ 33
(iii) Single-package air conditioners................... 30
(iv) Single-package heat pumps.......................... 33
(v) Small-duct, high-velocity systems................... 30
(vi) Space-constrained air conditioners................. 30
(vii) Space-constrained heat pumps...................... 33
------------------------------------------------------------------------
* * * * *
[FR Doc. 2015-23439 Filed 11-6-15; 8:45 a.m.]
BILLING CODE 6450-01-P
Office of the Federal Register, National Archives and Records Administration
Section
Proposed Rules
Action
Supplemental notice of proposed rulemaking.
Dates
DOE will accept comments, data, and information regarding this supplemental notice of proposed rulemaking (SNOPR) no later than December 9, 2015. See section V, ``Public Participation,'' for details.
Contact
Ashley Armstrong, U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, EE-2J, 1000 Independence Avenue SW., Washington, DC 20585-0121. Telephone: (202) 586-6590. Email: [email protected] Johanna Hariharan, U.S. Department of Energy, Office of the General Counsel, GC-33, 1000 Independence Avenue SW., Washington, DC, 20585- 0121. Telephone: (202) 287-6307. Email: [email protected]
FR Citation
80
FR
69277
RIN Number
1904-AB94
CFR Citation
10
CFR
429 10
CFR
430
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