Vol. 80 Monday, 
No. 216 November 9, 2015 
Part II 
Department of Energy 
10 CFR Parts 429 and 430 
Energy Conservation Program: Test Procedures for Central Air Conditioners and Heat Pumps; Proposed Rule 
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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. 
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: RCAC-HP-2009-TP-0004@
ee.doe.gov. 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: Ashley.Armstrong@ee.doe.gov . 
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: Johanna.Hariharan@hq.doe.gov . 
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: Brenda.Edwards@ee.doe.gov. 
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- 
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1Where 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. 
2For editorial reasons, upon codification in the 
U.S. Code, Part B was re-designated Part A. 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
1with 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)) 
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 
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3Available at: http://energy.gov/sites/prod/files/
2014/07/f17/
Enforcement%20Policy%20Statement%20- %20cac%20off%20mode.pdf (Last accessed March 
30, 2015.) 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. 
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 
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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 (P
X); 
(4) Changing of the calculation of the 
off mode power rating (P W,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; 
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4Conventional 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) 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 (C
D); 
(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 
(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 °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 
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5DOE 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. 
6Available at: www.ahrinet.org/App _Content/
ahri/files/Certification/OM%20pdfs/USE_ OM.pdf 
(Last accessed March 20, 2015.) 
7According 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.) 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 
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).
6This document specifies the 
following definitions: 
A Split System BMG [Basic Model Group7] 
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. 
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 
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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 P
W,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 
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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 
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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—T ESTREQUIREMENTS FOR SINGLE -SPLIT-SYSTEM NON-SPACE -CONSTRAINED AIRCONDITIONERS RATED BY  
OUM S 
Date Equipment type Must test each: With: 
Before the compliance date 
for any amended energy 
conservation standards.Split-System AC with sin-
gle capacity condensing unit.Model of Outdoor Unit ....... 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. 
Split-System AC with other 
than single capacity con-densing unit.Model of Outdoor Unit ....... 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, 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 amended energy conservation standards.Split-system AC ................. Model of Outdoor Unit ....... The model of blower coil indoor unit that is likely to 
have the largest volume of retail sales with the par-ticular 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 
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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—E XAMPLE RATINGS FOR MULTI-SPLITSYSTEMS  
Basic model Individual model 
(outdoor unit) Individual model 
(indoor unit) Sample size Ducted rating Non-ducted 
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 
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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 
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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. 
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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: 
Basic model Individual model # (outdoor unit) Individual model # (indoor unit) Certified rating 
(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: 
Equipment type Basic model number Individual model number(s) 
1 2 3 
Single Package ............................. Number unique to the basic 
model.Package ............ N/A .................... N/A. 
Split System (rated by OUM) ....... Number unique to the basic 
model.Outdoor Unit ..... Indoor Unit(s) .... Air Mover (or N/A if rating coil- 
only system or fan is part of in-
door unit model number). 
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Equipment type Basic model number Individual model number(s) 
1 2 3 
Outdoor Unit Only ......................... Number unique to the basic 
model.Outdoor Unit ..... N/A .................... N/A. 
Split-System or SDHV (rated by 
ICM).Number unique to the basic 
model.Outdoor Unit ..... Indoor Unit(s) .... N/A. 
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 °F, and whether the optional H4
2low temperature test 
was used to characterize performance at temperatures below 17 °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—R OUNDING PROPOSALS  
Measure 10 CFR 430.23 
(one unit) 10 CFR 429.16 
(sample) 
Cooling capacity/heating capacity: 
<20,000 Btu/h ............................................. nearest 50 Btu/h ............................................... neares t 100 Btu/h. 
≥20,000 Btu/h and <38,000 Btu/h .............. nearest 100 Btu/h ............................................. nearest 200 Btu/h. 
≥38,000 Btu/h and <65,000 Btu/h .............. nearest 250 Btu/h ............................................. nearest 500 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 (%). 
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8Unless 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. 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 (C
D) value used 
to determine efficiency ratings. In this proposal, DOE would run C
Dtesting 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)
8AAON, Inc. (AAON) supported 
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9A Voluntary Industry Certification Program, or 
VICP, is an independent, third-party program that 
conducts ongoing verification testing of members’ products. 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. 
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),
9or 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) 
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 
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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 
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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 
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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 
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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 
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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—A CTIVE WAIVERS AND ACTIVE INTERIM WAIVERS  
Air Conditioners and Heat Pumps, Consumer 
Scope Decision & order Termination 
ECR International, Inc., Multi-zone Unitary Small Air Conditioners and Heat Pumps (Petition & Interim Waiver, 78 FR 47681, 
8/6/2013).III.C.2 
Daikin AC (Americas), Inc., Heat Pump & Water Heater Combination ....................... 76 FR 11438, 3/2/2011 ................... .......... III.C.1 
Daikin AC (Americas), Inc., Heat Pump & Water Heater Combination ....................... 75 FR 34731, 6/18/2010 .................. ......... III.C.1 
Hallowell International, Triple-Capacity Northern Heat Pumps ................................... 75 FR 6013, 2/5/2010 ............ ................... III.C.4 
Cascade Group, LLC, Multi-blower Air-Conditioning and Heating Equipment ............ 73 FR 50787, 8/28/2008 ...................... ..... III.C.3 
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—T ERMINATED WAIVERS  
Scope Decision & order 
Daikin U.S. Corporation, Multi-split Heat Pumps and Heat Recovery Systems ...... 73 FR 39680, 7/10/2008. 
Mitsubishi Electric and Electronics USA, Inc., Variable Refrigerant Flow Zoning 
Air Conditioners and Heat Pumps.72 FR 17528, 4/9/2007. 
Fujitsu General Limited, Multi-split Products ............................................................ 72 FR 71383, 12/17/200 7. 
Samsung Air Conditioning, Multi-split Products ........................................................ 72 FR 71387, 12/17/2007. 
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- 
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10When 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. 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.
10In 
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. 
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 
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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 (P
W,OFF ) on an 
average of wattages P1 and P2, which 
would be recorded at the different 
outdoor ambient temperatures of 82 °F and 57 °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 °F test point could create a loophole wherein a crankcase heater could be designed to turn on just below 57 °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 °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 °F below the point at which the crankcase heater turns on (‘‘on’’ set point temperature) and the other off mode test 3–5 °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 
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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 °F below the ‘‘on’’ set point temperature, at 47 °F, and at 17 °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 °F above the manufacturer’s reported ‘‘off’’ set point and measure P2 at a temperature that is 
3–5 °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 °F below the ‘‘on’’ set point temperature, 47 °F, and 17 °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 °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 °F below the temperature at which the manufacturer specifies the crankcase heater turns on. The third test would be conducted at 5 °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 °F below the heater turn-on temperature and at 3–5 °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 °F with a test at 72±2 °F and 
replace the off mode test at 57 °F with a test at a temperature which is 5±2 °F 
below a manufacturer-specified turn-on temperature. This approach maintains the intent of the off mode power consumption rating (P
W,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 °F test point. 
DOE does not propose to adopt an 
additional test point at a temperature of 17 °F, as recommended by the 
stakeholders; (Efficiency Advocates, No. 35 at p. 4; AHRI, No. 41 at p. 2) at a temperature 5 °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 °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 (P
W,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 
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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, P
x, 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 P
xnot 
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 P
xis not repeated. DOE 
proposes to require that the measurement of P
xoccur after the 
measurement of the heating season total off mode power, P2
x, 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 P
xis 
being measured. Since P xmeasures 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 P
x. 
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: 
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respectively. 76 FR 65616, 65629–30 
(Oct. 24, 2011). P1 Dis the off mode 
power with the crankcase heater 
disconnected, which is equal to the low- voltage power, P
x. P1 xis the shoulder- 
season total off mode power, P2 xis 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 P
x) 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 P
x 
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 = P2
x¥ PxiP1 = 
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: 
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 P
W,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 
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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, P
W,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 P
W,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 P
W,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 
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11Or heating capacity for heating-only heat 
pumps. 12Such a requirement does not exist for heating- 
only heat pumps. 
13For 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. 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
11and 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). 
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.
13This 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. 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 A
2test 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. 
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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 °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 °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 °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 
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14The 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. 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.
14Electronic 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 
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15The range of superheating temperatures was 
generalized from industry-accepted practice and 
state-level authority regulations on refrigerant charging for non-TXV systems. 
16The 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. 
17The range of subcooling temperatures was 
generalized from manufacturer-published and 
technician-provided service instructions and are typical of industry practice. 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. 
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 A
2test condition, requiring 
addition of charge until the superheat temperature measured at the suction line upstream of the compressor is 12 °F with tolerance discussed in section III E.14.
15For 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 A
2condition, 
requiring addition of charge until the subcooling
16temperature measured at 
the condenser outlet is 10 °F with tolerance discussed in section III E.14.
17 
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 H1
2condition. DOE also 
proposes that charging be done for the H1 or H1
2test 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 A
2test 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 
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proposes a maximum permissible 
variation in temperature measured at this location during the OFF period of ±1.0 °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 °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, C/_128, 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, C/_129, 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 (C
D) 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 C
Dvalues range from 0.02 to 
0.18, with an average of 0.09. It also found no correlation between C
Dand 
SEER, EER, or cooling capacity. DOE also reviewed the AHRI 210/240-Draft (see section III.E.14), which updates the cooling C/_128 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 C/_128 value in Appendix M to 0.2. At this 
time, DOE is not proposing to update the default heating C/_129 value. In 
evaluating appropriate default values, DOE also reviewed its testing requirements to measure C
D. 
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 C/_128 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 C/_128, 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 C/_128, 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 C/_128 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 C/_128 of the last three cycles 
are within 0.02 of or lower than the previous three cycles, use the average C/_128 of all valid cycles. After the fifth 
valid cycle, if the average C/_128 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 C
Dfor 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 
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18Khalifa, H.E. ‘‘Break-in Behavior of Scroll 
Compressors’’ (1996). International Compressor 
Engineering Conference. Paper 1145. 19Ibid. pp. 442–443. 20ANSI/AHRI 210/240–2008 with Addendum 2 
is named as such but includes changes per an Addendum 1 on the same standard. 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,
18and 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. 
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.
19Moreover, 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. 
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.
20The 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. 
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 
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21ASHRAE 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. 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 
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 
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(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. 
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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 °F outdoor dry bulb temperature and 80 °F dry bulb, 67 °F wet bulb indoor conditions, and for outdoor units as the lowest cooling capacity listed in published product literature for these 
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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. 
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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—P ROPOSALS FROM PRIOR NOTICES ADOPTED WITHOUT MODIFICATION IN THISSNOPR 
Section Proposal to . . . Reference Action Preamble discus-
sion Regulatory text 
location * 
June 2010 NOPR 
A.7 .................. Add Calculations for Sensible Heat 
Ratio.75 FR 31229 ......... Upheld ................... III.I.5 ...................... 3.3c, 4.6. 
A.10 ................ Add Definitions Terms Regarding 
Standby Power.75 FR 31231 ......... Upheld ................... None ...................... Definitions. 
B.4 .................. Allow a Wider Tolerance on Air Volume 
Rate To Yield More Repeatable Lab-
oratory Setups.75 FR 31233 ......... Upheld ................... None ...................... 3.1.4.1.1a.4b. 
B.5 .................. Change the Magnitude of the Test Op-
erating Tolerance Specified for the External Resistance to Airflow.75 FR 31234 ......... Upheld ................... None ...................... 3.3d Table, 3.5h Table, 3.7a Table, 
3.8.1 Table, 3.9f Table. 
Change the Magnitude of the Test Op-
erating Tolerance Specified for the Nozzle Pressure Drop.75 FR 31234 ......... Upheld ................... None ...................... 3.3d Table, 3.5h Table, 3.7a Table, 
3.8.1 Table. 
B.6 .................. Modify Refrigerant Charging Proce-
dures: Disallow Charge Manipulation after the Initial Charge.75 FR 31234 ......... Upheld ................... III.E.7 ..................... 2.2.5. 
B.7 .................. Require All Tests be Performed with 
the Same Refrigerant Charge Amount.75 FR 31235, 
31250.Upheld ................... III.F.1 ..................... 2.2.5.8. 
B.8 .................. When Determining the Cyclic Degrada-
tion Coefficient CD, Correct the In-door-Side Temperature Sensors Used During the Cyclic Test To Align With the Temperature Sensors Used During the Companion Steady-State Test, If Applicable: Equation.75 FR 31235 ......... Upheld ................... None ...................... 3.4c, 3.5i, 3.7e, 3.8. 
When Determining the Cyclic Degrada-
tion Coefficient CD, Correct the In-door-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.75 FR 31236 ......... Upheld ................... None ...................... 3.3b, 3.7a, 3.9e, 3.11.1.1, 3.11.1.3, 
3.11.2a. 
B.9 .................. Clarify Inputs for the Demand Defrost 
Credit Equation.75 FR 31236 ......... Upheld ................... None ...................... 3.9.2a. 
B.10 ................ Add Calculations for Sensible Heat 
Ratio.75 FR 31237 ......... Upheld ................... III.I.5 ...................... 3.3c, 4.6. 
B.11 ................ Incorporate Changes To Cover Testing 
and Rating of Ducted Systems Hav-ing More Than One Indoor Blower.75 FR 31237 ......... Upheld ................... III.C.3 ..................... 2.2.3, 2.2.3b, 2.4.1b, 3.1.4.1.1d, 
3.1.4.2e, 3.1.4.4.2d, 3.1.4.5.2f, 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 Cover Triple-Capac-
ity, Northern Heat Pumps.75 FR 31238 ......... Upheld ................... III.C.4 ..................... 3.6.6, 4.2.6. 
B.13 ................ Specify Requirements for the Low-Volt-
age Transformer Used When Testing for Off-Mode Power Consumption.75 FR 31238 ......... Upheld ................... III.F.1 ..................... 2.2d. 
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TABLE III.6—P ROPOSALS FROM PRIOR NOTICES ADOPTED WITHOUT MODIFICATION IN THISSNOPR—Continued 
Section Proposal to . . . Reference Action Preamble discus-
sion Regulatory text 
location * 
B.14 ................ Add Testing Procedures and Calcula-
tions for Off Mode Power Consump-
tion.75 FR 31238 ......... Upheld ................... III.D ........................ Definitions, 3.13, 4.3, 4.4. 
April 2011 SNOPR 
III.A ................. Revise Test Methods and Calculations 
for Off-Mode Power and Energy Consumption.76 FR 18107 ......... Upheld ................... III.D ........................ Definitions, 3.13, 4.3, 4.4. 
III.B ................. Revise Requirements for Selecting the 
Low-Voltage Transformer Used Dur-ing Off-Mode Test(s).76 FR 18109 ......... Upheld ................... III.F.1 ..................... 2.2d. 
III.D ................. Add Calculation of the Energy Effi-
ciency Ratio for Cooling Mode Steady-State Tests.76 FR 18111 ......... Upheld ................... None ...................... 4.7. 
III.E ................. Revise Off-Mode Performance Ratings 75 FR 31238 ......... Upheld ................... III.D ........................ Definitions, 3.13, 4.3, 4.4. 
October 2011 SNOPR 
III.A ................. Reduce Testing Burden and Com-
plexity.76 FR 65618 ......... Upheld ................... III.D ........................ Definitions, 3.13, 4.3, 4.4. 
III.B ................. Add Provisions for Individual Compo-
nent Testing.76 FR 65619 ......... Upheld ................... III.D ........................ Definitions, 3.13, 4.3, 4.4. 
III.C ................. Add Provisions for Length of Shoulder 
and Heating Seasons.76 FR 65620 ......... Upheld ................... III.D ........................ Definitions, 3.13, 4.3, 4.4. 
III.D ................. Revise Test Methods and Calculations 
for Off-Mode Power and Energy Consumption.76 FR 65620 ......... Upheld ................... III.D ........................ Definitions, 3.13, 4.3, 4.4. 
III.D.1 .............. Add Provisions for Large Tonnage Sys-
tems.76 FR 65621 ......... Upheld ................... III.D ........................ Definitions, 3.13, 4.3, 4.4. 
III.D.2 .............. Add Requirements for Multi-Com-
pressor Systems.76 FR 65622 ......... Upheld ................... III.D ........................ Definitions, 3.13, 4.3, 4.4. 
* Section numbers in this column refer to the proposed Appendix M test procedure in this notice. 
TABLE III.7—P ROPOSALS FROM PRIOR NOTICES WITHDRAWN OR AMENDED IN THISSNOPR ORPROPOSED NOCHANGE  
TO THE TESTPROCEDURE  
Section Proposal to . . . Reference Action Preamble discus-
sion Regulatory text 
location * 
June 2010 NOPR 
A.1 .................. Set a Schedule for Coordinating the 
Publication of the Test Procedure and Energy Conservation Standards.75 FR 31227 ......... No Change ** ......... None ...................... None. 
A.2 .................. Bench Testing of Third-Party Coils ....... 75 FR 31227 ......... No Change ** ......... None ..................... . None. 
A.3 .................. No Change to Default Values for Fan 
Power.75 FR 31227 ......... Amended ............... III.H.3 ..................... 10 CFR Part 430, Subpart B, Appendix 
M1 3.3d, 3.5.1, 3.7c, 3.9.1b. 
A.4 .................. No Change to External Static Pressure 
Values.75 FR 31228 ......... Amended ............... III.H.1 ..................... 10 CFR Part 430, Subpart B, Appendix 
M1 3.1.4.1.1c. Table. 
A.5 .................. No Conversion to Wet-Coil Cyclic Test-
ing.75 FR 31228 ......... No Change ** ......... III.I.4 ...................... None. 
A.6 .................. No Change to Test Procedure for Test-
ing Systems with ‘‘Inverter-Driven Compressor Technology’’.75 FR 31229 ......... No Change ** ......... None ...................... None. 
A.8 .................. Regional Rating Procedure ................... 75 FR 31229 ......... Withdrawn † ........... None ...................... None. 
A.9 .................. Modify Definition of Tested Combina-
tion.75 FR 31230 ......... Amended ............... III.F.2 ..................... 10 CFR 430.2 Definitions. 
Add Minimum ESP for Short Duct Sys-
tems.75 FR 31230 ......... Amended ............... III.F.2 ..................... 3.1.4.1.1c. Table. 
Clarify That Optional Tests May Be 
Conducted without Forfeiting Use of the Default Value(s).75 FR 31230 ......... Withdrawn † ........... None ...................... None. 
B.1 .................. Modify the Definition of ‘‘Tested Com-
bination’’.75 FR 31231 ......... Amended ............... III.F.2 ..................... 10 CFR 430.2 Definitions. 
B.2 .................. Add Minimum ESP for Short Duct Sys-
tems.75 FR 31232 ......... Amended ............... III.F.2 ..................... 3.1.4.1.1c. Table. 
Add Indoor Unit Design Characteristics 
for Limiting Application of Minimum ESP for Short Duct Systems.75 FR 31232 ......... Amended ............... III.F.2 ..................... 3.1.4.1.1c. Table header. 
B.3 .................. Clarify That Optional Tests May Be 
Conducted Without Forfeiting Use of the Default Value(s).75 FR 31233 ......... Withdrawn † ........... None ...................... None. 
B.6 .................. No Adoption of Requirement of Manu-
facturer Sign-Off after Charging Re-frigerant.75 FR 31234 ......... No Change ** ......... None ...................... None. 
B.7 .................. Allow Interactions between Manufactur-
ers and Third-Party Testing Labora-tory.75 FR 31235 ......... Withdrawn ............. III.F ........................ None. 
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22Table 3 of 10 CFR 430 Subpart B Appendix M 
2310 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. TABLE III.7—P ROPOSALS FROM PRIOR NOTICES WITHDRAWN OR AMENDED IN THISSNOPR ORPROPOSED NOCHANGE  
TO THE TESTPROCEDURE —Continued 
Section Proposal to . . . Reference Action Preamble discus-
sion Regulatory text 
location * 
B.15 ................ Add Parameters for Establishing Re-
gional Standards.75 FR 31239 ......... Withdrawn † ........... None ...................... None. 
B.15a .............. Use a Bin Method for Single-Speed 
SEER Calculations for the Hot-Dry Region and National Rating.75 FR 31240 ......... Withdrawn † ........... None ...................... None. 
B.15b .............. Add New Hot-Dry Region Bin Data ...... 75 FR 31240 ......... Withdrawn † ........... None ...................... None . 
B.15c .............. Add Optional Testing at the A and B 
Test Conditions With the Unit in a Hot-Dry Region Setup.75 FR 31241 ......... Withdrawn † ........... None ...................... None. 
B.15d .............. Add a New Equation for Building Load 
Line in the Hot-Dry Region.75 FR 31242 ......... Withdrawn † ........... None ...................... None. 
B.16 ................ Add References to ASHRAE 116–1995 
for Equations That Calculate SEER and HSPF for Variable Speed Sys-tems.75 FR 31243 ......... Withdrawn ............. III.E.13 ................... None. 
B.17 ................ Update Test Procedure References ..... 75 FR 31243 ......... Amended ............... III.E.12 ................... 10 CFR 430.3 Definitions. 
April 2011 SNOPR 
III.C ................. Withdraw of the Proposal To Add the 
New Regional Performance Metric SEER Hot-Dry.76 FR 18110 ......... No Change ** ......... None ...................... None. 
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. † 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. 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 
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24Docket No. EERE–2010–BT–TP–0010–0043. 25Siegel, 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. 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). 
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.
25From 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. 
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 
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26Docket No. EERE–2014–BT–STD–0048. 
27DOE did not increase the ESP requirement for 
small-duct, high-velocity units because the existing 
values in the test procedure represent field operations. 28See 10 CFR 430 Subpart B Appendix M section 
3.3.d. 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. 
TABLE III.8—P ROPOSED MINIMUM ESP 
REQUIREMENTS FOR CENTRAL AIR 
CONDITIONERS AND HEAT PUMPS  
OTHER THAN MULTI-SPLIT SYSTEMS  
AND SMALL -DUCT, H IGH-VELOCITY  
SYSTEMS27 
Rated cooling or heating capac-
ity 
(Btu/h) Minimum 
ESP 
(in. wc.) 
Up Thru 28,800 .......................... 0.45 
29,000 to 42,500 ........................ 0.50 
43,000 and Above ...................... 0.55 
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.
28The 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. 
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 
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29See 10 CFR 430 Subpart B Appendix M Section 
1. Definitions. 
30Erbs, 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. 
31Francisco, 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. 
32Fairey, 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. 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 °F outdoor temperature. 
The heating load is also proportional to the difference between 65 °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 °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 
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.
30In 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 °F. (NEEA & NPCC, No. 19 at p. 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 °F, while the typical balance point is in the range 26 to 32 °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 °F ambient, which is higher than the typical 50–60 °F zero load point,
31causes 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).
32For these reasons, DOE 
reviewed the choice of heating load line for HSPF ratings and proposes to modify it. 
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33ORNL, 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). 34Most commonly used heating load equation 
based on minimum design heating requirement and 
region IV: Q h(47) * 0.77*(65–Tj)/60. 35See ANSI/AHRI Standard 340/360–2007 with 
Addenda 1 and 2, Performance rating of commercial and industry unitary air-conditioning and heat pump equipment. 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.
33In 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. 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 
Tj= the outdoor bin temperature, °F 
TOD= the outdoor design temperature, °F 
DHR = the design heating requirement, 
Btu/h 
Tzl= the zero load temperature, °F 
The proposed equation includes the 
following changes from the current heating load line used for calculation of HSPF:
34 •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 °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—G ENERALIZED 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, T ZL........................................................................................... 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 °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 °F and heating bin data at 62 °F. This results in a dead band of 5 °F. Because the current test procedure prescribes the indoor temperature set point to be 70 °F for heating, and 80 °F for cooling, the temperature difference of 10 °F is inconsistent with the dead band of 5 °F from the temperature bin. University of Alabama also suggested adopting 62 °F and 52 °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 °F for heating and 80 °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 
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 °F. Given the cooling-mode zero load point of 65 °F, the proposed change would increase the temperature difference between the heating and cooling zero load points to 10 °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 °F instead of 62 °F, as required by the current test 
procedure (see Appendix M, section 3.6.4 Table 11). The test would still be 
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36Larson, 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. 37All temperatures in section III.H.5, if not noted 
otherwise, mean outdoor temperature. 38Rice et al. (2015) Review of Test Procedure for 
Determining HSPFs of Residential Variable-Speed Heat pumps. (Docket No. EERE–2009–BT–TP– 0004–0047). conducted using minimum compressor 
speed. With the modified heating load line there would be no heat pump operation at 62 °F, so cyclic testing at 47 °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. 
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 °F and 62 °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 °F and at 17 °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. 
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 °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 °F. In the mid-range outdoor temperature range (17–47 °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 °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 °F would be determined by the minimum speed tests at 47 °F and the intermediate speed test at 35 °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 °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 °F would be determined by minimum speed tests at 47 °F and at 35 °F, where the test point of minimum speed at 35 °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 °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 °F and the intermediate speed test at 35 °F to determine the intermediate capacity and the corresponding energy usage, where the test at the medium speed at 17 °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 °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 °F and minimum speed at 35 °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 °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%.
38DOE believes that this 
indicates that the modified heating load 
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39In the case that the low cutoff temperature is 
higher than 12 °F, the manufacturer would not be allowed to utilize this option for calculation of the 
maximum heating load capacity. 40EERE–2009–BT–TP–0004–0047. 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. 
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 °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 °F and at 17 °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 °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 °F and have a low cutoff temperature less than 12 °F, the manufacturer could choose to calculate the maximum heating capacity and the corresponding energy usage through two maximum speed tests at: (1) 17 °F outdoor temperature, and (2) 2 °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 °F or at a low cutoff temperature, whichever is higher. 
The testing done by ORNL found that 
the unit efficiency at maximum speed below 17 °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 °F, but also for those that do not.
40DOE therefore proposes to revise 
Appendix M1 such that, for variable speed units that do not limit maximum speed operation below 17 °F, manufacturers would also have the option to use this revised method if it is more representative of low ambient performance. 
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 °F, the maximum speed performance at 35 °F is required. However, the maximum speed 35 °F test is not required and performance at 35 °F may instead be calculated from the two maximum speed tests at 17 °F and 47 °F. Therefore, even though manufacturers who choose to rate with the optional low ambient point would no longer need the maximum speed 47 °F point to calculate energy use at maximum speed below 17 °F, they would need either the maximum speed 47 °F test point or 35 °F test point to calculate the capacity and energy use at maximum speed at 35 °F. They may also wish to conduct the maximum speed 47 °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 °F, manufacturers would test at both maximum speed at 2 °F (or low cutoff temperature) and maximum speed at 17 °F. For rating at 35 °F, they would also test at either 
maximum speed at 35 °F or maximum speed at 47 °F. Finally, to rate heating capacity or nominal heating capacity (for units whose controls do not allow maximum speed operation at 47 °F), they may also choose to test at either maximum speed at 47 °F allowed by their standard controls or cooling capacity maximum speed at 47 °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—P ROPOSED MAXIMUM SPEED HEATING TESTCOMBINATION OPTIONS FOR UNITS HAVING A VARIABLE -SPEED  
COMPRESSOR  
Test description (out-
door dry bulb tempera-
tures) Current test procedure 
(Option 1) Option 2 Option 3 Option 4 Option 5 
H1N(2 °F) .................... optional if using nomi-
nal heating capacity......................... ...................................... for nominal heating ca-
pacity.for nominal heating ca-
pacity. 
H12(47 °F) ................... X .................................. X for heating capacity 
only....................................... X. 
H22(35 °F) ................... ...................................... ........................ X .................................. X ..................................
H32(17 °F) ................... X .................................. X X .................................. X ................................. . X. 
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TABLE III.10—P ROPOSED MAXIMUM SPEED HEATING TESTCOMBINATION OPTIONS FOR UNITS HAVING A VARIABLE -SPEED  
COMPRESSOR —Continued 
Test description (out-
door dry bulb tempera-
tures) Current test procedure 
(Option 1) Option 2 Option 3 Option 4 Option 5 
H42(2 °F) * ................... ...................................... X X .................................. X .................................. X. 
* Or low cutoff temperature, whichever is higher. 
Note: For units with a low cutoff temperature higher than 12 °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 
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41http://www.ahridirectory.org/ahridirectory/
pages/home.aspx. 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,
41manufacturers 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 °F and 
17°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. 
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 °F and 64.4 °F, instead of the current requirement of 80 °F and 67 °F, respectively. Heating indoor dry bulb temperature should use 68 °F instead of the current requirement of 70 °F. For the outdoor conditions, testing at 113 °F, 95 °F, and 77 °F have been proposed for the cooling mode, and 41 °F, 23 °F, and 5 °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 °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 °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 °F or 115 °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 °F/ 67 °F to 78 °F/61 °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 °F than others, but based on the current test procedure, there is no testing requirement for temperatures above 95 °F. For heat pumps, systems may perform differently above 47 °F and below 17 °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 °F and adding a test point for HSPF ratings at an outdoor temperature below 17 °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. 
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42AHRI Directory of Certified Product 
Performance: https://www.ahridirectory.org/
ahridirectory/pages/home.aspx. 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.
42DOE believes that these 
requirements will ensure that air volume rates used for rating central air conditioners and heat pumps are in an appropriate range. 
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 °F dry bulb and 67 °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, B
1, or B 2test condition 
(82 °F dry bulb, 65 °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 °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 °F dry bulb, 65 °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 °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 
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43IEC Standard 62301 covers measurement of 
power consumption for standby mode and low 
power modes, as defined therein. 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 °F dry bulb and 65 °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),
43and 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. 
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. 
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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 
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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 
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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 
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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. 
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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 
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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 72±2 °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 °F with a test at a temperature which is 5±2 °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 °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; 
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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 °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 A
2test condition, and for heating- 
only heat pumps refrigerant charging at the H 1or H1 2test condition, to meet a 
12 ± 2 °F superheat temperature 
requirement for units equipped with fixed orifice type metering devices and a 10 ± 2 °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 H
1or 
H1 2test condition after charging at the 
A or A 2test condition, and if non- 
functional, the proposal to adjust refrigerant charge to the requirements of the proposed standardized charging procedure at the H
1or H1 2test 
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 °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 
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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 °F instead of at 62 °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 °F and intermediate speed test at 35 °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 °F and at 35 °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 °F outdoor temperature or at low cutoff temperature, whichever is higher (in conjunction with the test at maximum speed at 17 °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 
■1. The authority citation for part 429 
continues to read as follows: 
Authority: 42 U.S.C. 6291–6317. 
■2. Amend § 429.12 by revising 
paragraphs (b)(8) and (12) to read as follows: 
§ 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 
* * * * * 
■3. Section 429.16 is revised to read as 
follows: 
§ 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 § 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. 
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Category Equipment type Must test each: With: 
Single-Package HP.
Space-Constrained Single- 
Package AC.
Space-Constrained Single- 
Package HP.
Outdoor Unit and Indoor 
Unit (Rated by OUM).Single-Split-System HP ..... Model of Outdoor Unit ....... The model of indoor unit that is likely to have the larg-
est volume of retail sales with the particular model 
of outdoor unit. 
Space-Constrained Split- 
System AC.
Space-Constrained Split- 
System HP.
Multi-Split, Multi-Circuit, or 
Single-Zone-Multiple-Coil Split System.Model of Outdoor Unit ....... At a minimum, a ‘‘tested combination’’ composed en-
tirely of non-ducted indoor units. For any models of outdoor units also sold with models of short-ducted indoor units, a second ‘‘tested combination’’ com-posed 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 mod-els 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 combina-tion 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 sec-
tion 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 amended energy 
conservation standards (with a compliance date after January 1, 2017).Split-System AC with sin-
gle capacity condensing unit.Model of Outdoor Unit ....... 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. 
Split-System AC with other 
than single capacity con-densing unit.Model of Outdoor Unit ....... 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, 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 any amended en-ergy conservation stand-ards with which compli-ance is required on or after January 1, 2017.Split-system AC ................. Model of Outdoor Unit ....... The model of blower coil indoor unit that is likely to 
have the largest volume of retail sales with the par-ticular 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: 
and x ¯is the sample mean; n is the number 
of samples; and x iis the ithsample; Or, 
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(ii) The upper 90 percent confidence 
limit (UCL) of the true mean divided by 
1.05, where: 
And x ¯is the sample mean; s is the sample 
standard deviation; n is the number of 
samples; and t 0.90is 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: 
and, x ¯is the sample mean; n is the number 
of samples; and x iis the ithsample; or, 
(ii) The lower 90 percent confidence 
limit (LCL) of the true mean divided by 0.95, where: 
And x ¯is the sample mean; s is the sample 
standard deviation; n is the number of 
samples; and t 0.90is 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 
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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 § 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 § 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 
§ 429.12 apply to central air conditioners and heat pumps. 
(2) Public product-specific 
information. Pursuant to § 429.12(b)(13), 
for each basic model (for single-package systems) or individual combination (for split-systems), a certification report 
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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 (P
W,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 °F dry bulb and 65 °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 § 429.12(b)(6) must consist of the following: 
Equipment type Basic model No. Individual model No(s). 
1 2 3 
Single Package ................. Number unique to the 
basic model.Package ............................ N/A .................................... N/A. 
Split System (rated by 
OUM).Number unique to the 
basic model.Outdoor Unit ...................... Indoor Unit(s) .................... Air Mover (or N/A if rating 
coil-only system or fan is 
part of indoor unit model number). 
Outdoor Unit Only ............. Number unique to the 
basic model.Outdoor Unit ...................... N/A .................................... N/A. 
Split-System or SDHV 
(rated by ICM).Number unique to the 
basic model.Outdoor Unit ...................... Indoor Unit(s) .................... N/A. 
(4) Additional product-specific 
information. Pursuant to § 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 C/_128 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 C/_129 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 °F, and whether the optional H4
2low temperature test 
was used to characterize performance at temperatures below 17 °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 § 429.70(e) of this subpart. 
■4. Amend § 429.70 by revising 
paragraph (e) to read as follows: 
§ 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 P
W,OFF ) pursuant to 
this section unless authorized pursuant to § 429.16(a)(2) and: 
(i) The AEDM is derived from a 
mathematical model that estimates the energy efficiency or energy 
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consumption characteristics of the 
individual combination (SEER, EER, HSPF, and/or P
W,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 § 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 § 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 § 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 § 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; 
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(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. 
* * * * * 
■5. Amend § 429.134 by adding 
paragraph (g) to read as follows: 
§ 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 § 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 C
Dvalue—(i) For 
central air conditioners and heat pumps other than models of outdoor units with no match, the C/_128 and/or C/_129 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 § 430.23(m) for each unit tested. The results of the measurement(s) for each C/_128 or C/_129 value 
will be compared to the C/_128 or C/_129 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 C/_128 or C/_129 value, 
the average measured C/_128 or C/_129 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 C/_128 
or C/_129 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 C/_128 and/or C/_129 value pursuant to 10 CFR part 
430. 
PART 430—ENERGY CONSERVATION 
PROGRAM FOR CONSUMER PRODUCTS 
■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. 
■7. Section 430.2 is amended by: 
■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 
■b. Revising the definitions of ‘‘basic 
model;’’ and ‘‘central air conditioner’’ to read as follows: 
§ 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 
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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. 
■8. Section 430.3 is amended by: 
■a. Revising paragraphs (c)(1) and 
(g)(2); 
■b. Adding paragraphs (c)(3) and (c)(4); 
■c. Removing paragraphs (g)(3); 
■d. Redesignating paragraphs (g)(4) 
through (g)(14) as (g)(3) through (g)(13); and 
■e. Revising newly redesignated (g)(3) 
through (g)(9). 
The revisions and additions read as 
follows: 
§ 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. 
* * * * * ■9. Section 430.23 is amended by 
revising paragraph (m) to read as 
follows: 
§ 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. 
* * * * * 
■10. Revise appendix M to subpart B of 
part 430 to read as follows: 
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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 P W,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 § 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 (C
D) means a 
parameter used in calculating the part load factor. The degradation coefficient for cooling is denoted by C
Dc. The degradation 
coefficient for heating is denoted by C Dh. 
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 
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 °F 
increments that are used to partition the outdoor dry-bulb temperature ranges of the cooling (≥65 °F) and heating (<65 °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 °F outdoor dry bulb temperature and 80 °F dry bulb, 67 °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 § 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 § 430.23 (m). For determination of certified rating requirements refer to § 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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Testing conditions Testing procedures Calculations 
Gen- Cool- Heat-
General General Cooling* Heating " era! ing . ing '' 
2 L 22a-c; 2.2.1; 2.2.4; 2.2.4.1; 
2.2.4.1 (!); 22.4.2; 2.2.5.1-5; 3.1; 3.1.1-3; 4.4; 
3.1.4.7; 3.1.10; 3.7a,b,d; 
Requirements for All units (except VRF) 2.2.5.7-8; 2.3; 2.3.1; 2.3.2; 2.4; 3.1.5-9; 3.11; I 3.3; 3.4; 3.5a-i 4.5; I 4.1 142 
3.Ra,d; 3.R.I; 3. 9; 3.1 CJ 
2.4.1 a,d; 2.5a-c; 2.5.1; 2.5.2- I 3.12 4.6 
2.5.42; 2.5.5 -2.13 
3.1.4.4.1; 3.1.4.4.2; 
3.1.4.1.1; 3.1.4.l.la,b; 
Single split-system- blower coil 2.2a(l) 3.1.4.4.3a-b; 3.1.4.5.1; 
3.1.42a-b; 3.1.4.3a-b 
3.1.4.5.2a-c; 3.1.4.6a-b 
3.1.4.4.1; 3.1.4.4.2; 
3.1.4.1. L 3.1.4.1. k 3.1.4.4.3c; 
Single split-system- coil-only 2.2a(l ); 2.2d,e;2.4d; 2.4.2 
3.1.4.2c; 3.5.1 3.1.4.52d; I :; 
Q, 
Q, 
" 3.7c; 3.8b; 3.9f; 3.9.1b '· " 9 
2.2a(2) " 'l'Ii-split = :> = " -s Outdoor unit with no match 2.2e 
" .... 
22.4.1(2); 2.2.5 6b; 2.4.1; 2.4.2 3.1.4.1.1; 3.1.4.1.1a,b; 
3.1.4.2a-h; 3. 1.4.3a-h 3.1.4.4.1; 3.1.4.4.2; 
3.1.4.4.3a-b; 3.1.4.5.1; 
3.1.4.5.2a-c; 3.1.4.6a-h :> 
"' g = " c I Singk-packagc 9 ·.5 " .... " ·s .... 
""' = " OJ] 
~ ..:: = 2.2.5.6.a ;; :> Heat pump = u 
3.1.7 3.1.4.1.1 Table 4 3.1.4.4.3 3 s 
"0 ~ Heating-only heat pump 
"0 ;., < [/'1 69348 Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules 
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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3.1.4.4.2c; 
Two-capacity northem heat pump 3.2.3c 3.6.3 
3.1.4.5.2 c-d 
Triple-capacity northern heat pump 3.2.5 3.6.6 4.2.6 
SDHV (non-VRF) 2.2b; 2.4.lc; 2.5.4.3 
3.1.4.4. I; 3. 1.4.4.2; 
Singk-.wne-mulli-coil ''Plil and non- 3.1.4.1.1; 3.1.4.l.la-b; 
2.2a( I ),(3 ); 2.2.3; 2.4. I h 3.1.4.4 3a-h; 3.1.4.5 I; 
VRF multiple-split with duct 3.1.4.2a-b; 3.1.4.3a-b 
3.1.4.5.2a-c; 3. 1.4.6a-h 
3.1.4.1.2; 3.1.4.2d; 
Single-zone-multi-coil split and non- 3.1.4.4.4; 3. 1.4.52e; 3.1.4.6c; 
2.2.a(l ),(3 ); 2.2.3 3.1.4.3c: 3 2.4c; 
VRF multiple-split, ductless 3.6.4.c; 3.8c 
3.5c,g,h; 3.5.2; 3.8c 
21: 2.2.a: 2.2.b: 2.2.c; 2.2.1; 2.2.2: 3.1 (except 3.3-3.5 3.7-3. ]() 4.4: 
VRF mulliple-splil t and 
2.2.3(a); 2.2.3(c);, 2.2.4; 2.2.5; 2.4- 3.1.3, 3.1.4) 4.5; 
4.1 4.2 
VRFSDHVt 2.12 3.1.4.1. k; 4.6 
3.11-3.13 
Singk sp..:..:d compr..:ssor, fixoo sp..:ed fan 3.2.1 3.6.1 4.1.1 4.2.1 
Single speed compressor, VA V fan 3.1.7 3.2.2 3.6.2 4.1.2 4.2.2 
£ Two-capacity compressor 3.1.10 3.2.3 3.6.3 4.1.3 4.2.3 
:E .. Variable speed compressor 3.2.4 3.6.4 4.1.4 4.2.4 
"'"" .. u 
Heat pump witlr heat comfmt controller 3.1.9 3.6.5 4.2.5 
~ " Units with a multi-speed outdoor fan 2.2.2 .... .a " " Single indoor nnit having multiple I"< 
"; 3.26 3.6.2: 3.6.7 4.1.5 4.2.7 
•;j blowers " ~ 69349 Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules 
† 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 § 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 § 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 § 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 § 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 § 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·ft
2· °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 × L
f× Wf× Nf÷ Q˙c(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. 
Q˙c(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 
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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 § 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 °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 °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 § 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 A
2test. 
(2) For cooling and heating heat pumps 
that do not function in the H1 or H1 2test 
with the charge set for the A or A 2test and 
for heating-only heat pumps, use the H1 or H1
2test. 
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 °F for fixed orifice systems or set subcooling to a target value of 10 °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 °F 
2. Subcooling: +/ ¥0.6 °F 
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3. High side pressure or corresponding 
saturation or dew point temperature: +/ ¥4.0 
psi or +/ ¥1.0 °F 
4. Low side pressure or corresponding 
saturation or dew point temperature: +/ ¥2.0 
psi or +/ ¥0.8 °F 
5. High side temperature: +/ ¥2.0 °F 
6. Low side temperature: +/ ¥2.0 °F 
7. Approach temperature: +/ ¥1.0 °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 
A2test, the conditions are not within the 
range specified in manufacturer’s 
instructions for the H1 or H1 2test, 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 A
2test 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·ft
2· °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 § 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—S IZE OF OUTLET PLENUM  
Cooling full-load air vol-
ume rate 
(scfm) Maximum 
diameter * 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, cal-
culate 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 § 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. 
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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 § 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 °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 · ft
2· °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 · ft
2· °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 § 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 § 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 · ft
2· °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 
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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 § 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 § 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 § 430.3). The temperature sensor (wick removed) must be accurate to within ±0.2 °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 °F when operated 
at conditions that result in the evaluation of dew points above 35 °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 § 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 § 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 § 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 § 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 
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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 °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 °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 § 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 § 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 § 430.3). The maximum and minimum temperatures measured by these sensors may differ by no more than 1.5 °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 ·ft
2·°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 § 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, A
2, A1, B, B 2, B1, C, 
C1, EV, F 1, G1, H0 1, H1, H1 2, H1 1, HI N, H3, 
H3 2, and H3 1Tests), 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 § 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 H
2O 
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 
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section. First, when conducting the A or A 2 
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 Q
Var, defined as follows, greater than 10 
percent. 
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 A
2Test, 
(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—M INIMUM EXTERNAL STATIC PRESSURE FOR DUCTED SYSTEMS TESTED WITH AN INDOOR BLOWER INSTALLED  
Rated cooling1or 
heating2capacity 
(Btu/h) Minimum external resistance3(inches of water) 
Short ducted sys-
tems4 Small-duct, high- 
velocity sys-
tems45 All other systems 
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 
1For 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 A2Test conditions. 
2For 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. 
3For ducted units tested without an air filter installed, increase the applicable tabular value by 0.08 inches of water. 
4See section 1.2, Definitions, to determine if the equipment qualifies as a short-ducted or a small-duct, high-velocity system. 
5If 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, DP
st_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. 
Where: 
DPst_i= target minimum external static 
pressure for test i; 
DPst_full= minimum external static pressure 
for test A or A 2(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 
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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 A
1, B1, C1, F1, and G 1Tests)— 
at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation Q
Var, 
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 E
VTest at an external static pressure that 
does not cause an automatic shutdown of the indoor blower or air volume rate variation Q
Var, 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 E
VTest 
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 A
2) and the H1 (or H1 2) Tests; 
2. Ducted heat pumps tested with constant- 
air-flow indoor blowers installed that provide the same air flow for the A (or A
2) and the 
H1 (or H1 2) 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 Q
Var, 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 A
2) 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 Q
Var, 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 H1
2 
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 
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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 Q
Var, 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 H1
2Test, (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 A
1and the H1 1tests; 2. Ducted heat pumps tested with constant- 
air-flow indoor blowers installed that provide 
the same air flow for the A 1and the H1 1 
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 Q
Var, 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 A
1cooling 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 H0
1, 
H1 1, H2 1, and H3 1Tests)—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 Q
Var, 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 H2
VTest at an external static 
pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation Q
Var, 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 H2
VTest 
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 
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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 °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°F of the required inlet conditions. 
3.1.6 Air volume rate calculations. For all steady-state tests and for Frost 
Accumulation (H2, H2
1, H2 2, H2 V) 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 § 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: 
Where, 
VÔ
s= air volume rate of standard (dry) air, (ft3/ 
min) da 
VÔ
mx= air volume rate of the air-water vapor 
mixture, (ft3/min) mx 
vn′ = specific volume of air-water vapor 
mixture at the nozzle, ft3per 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/ft3) 
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
3per lbm of dry air. 
(Note: In the first printing of ASHRAE 
Standard 37–2009, the second IP equation for Q
mishould read, 
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 A
2Test 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 H1
2Test 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 E
VTest, and the first test using the 
Heating Minimum Air Volume Rate must precede the H2
VTest. 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 °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 °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 H1
2 
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, T
CC. 
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, C
Dc. If testing 
outdoor units of central air conditioners or heat pumps that are not sold with indoor units, assign C
Dcthe default value of 0.2. 
Table 4 specifies test conditions for these four tests. 
TABLE 4—C OOLING MODETESTCONDITIONS FOR UNITS HAVING A SINGLE -SPEED COMPRESSOR AND A FIXED-SPEED  
INDOOR BLOWER , ACONSTANT AIRVOLUME RATEINDOOR BLOWER , ORNOINDOOR BLOWER  
Test description Air entering indoor unit tem-
perature (°F) Air entering outdoor unit tem-
perature (°F) Cooling air volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
A Test—required (steady, wet coil) ......... 80 67 95 175 Cooling full-load.2 
B Test—required (steady, wet coil) ......... 80 67 82 165 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) 
1The specified test condition only applies if the unit rejects condensate to the outdoor coil. 
2Defined in section 3.1.4.1. 
3The 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 °F or less be used.) 
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4Maintain 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 A
2, A1, B2, and B 1Tests. Use the two dry- 
coil tests, the steady-state C 1Test and the d 
D1Test, to determine the cooling mode cyclic 
degradation coefficient, C Dc. 
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—C OOLING MODETESTCONDITIONS FOR UNITS WITH A SINGLE -SPEED COMPRESSOR THATMEET THE SECTION  
3.2.2.1 I NDOOR UNITREQUIREMENTS  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Cooling air volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
A2Test—required (steady, wet coil) ........ 80 67 95 175 Cooling full-load.2 
A1Test—required (steady, wet coil) ........ 80 67 95 175 Cooling minimum.3 
B2Test—required (steady, wet coil) ........ 80 67 82 165 Cooling full-load.2 
B1Test—required (steady, wet coil) ........ 80 67 82 165 Cooling minimum.3 
C1Test4—required (steady, dry coil) ...... 80 (4) 82 ........................ Cooling minimum.3 
D1Test4—required (cyclic, dry coil) ........ 80 (4) 82 (5) 
1The specified test condition only applies if the unit rejects condensate to the outdoor coil. 
2Defined in section 3.1.4.1. 
3Defined in section 3.1.4.2. 
4The 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 °F or less be used.) 
5Maintain 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 1Test. 
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 A 2, B2, B1, and F 1Tests. Use the two dry- 
coil tests, the steady-state C 1Test and the 
cyclic D 1Test, to determine the cooling-mode 
cyclic-degradation coefficient, C Dc. 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 B
1 
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 C
2Test 
and the cyclic D 2Test, to determine the 
cooling-mode cyclic-degradation coefficient that only applies to on/off cycling from high 
capacity, C
Dc(k=2). The default C Dc(k=2) is 
the same value as determined or assigned for the low-capacity cyclic-degradation coefficient, C
Dc[or equivalently, C Dc(k=1)]. 
TABLE 6—C OOLING MODETESTCONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor 
capacity Cooling air 
volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
A2Test—required (steady, wet 
coil).80 67 95 175 ................... High ................... Cooling Full- 
Load.2 
B2Test—required (steady, wet 
coil).80 67 82 165 ................... High ................... Cooling Full- 
Load.2 
B1Test—required (steady, wet 
coil).80 67 82 165 ................... Low .................... Cooling Min-
imum.3 
C2Test—required (steady, dry- 
coil).80 (4) 82 High .................. Cooling Full- 
Load2.
D2Test—required (cyclic, dry-coil) 80 (4) 82 High .................. (5) ......................
C1Test—required (steady, dry- 
coil).80 (4) 82 Low ................... Cooling Min-
imum3.
D1Test—required (cyclic, dry-coil) 80 (4) 82 Low ................... (6) ......................
F1Test—required (steady, wet 
coil).80 67 67 153.5 ................. Low .................... Cooling Min-
imum.3 
1The specified test condition only applies if the unit rejects condensate to the outdoor coil. 
2Defined in section 3.1.4.1. 
3Defined in section 3.1.4.2. 
4The 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 °F or less. 
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5Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the C 2Test. 
6Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the C 1Test. 
3.2.4 Tests for a unit having a variable- 
speed compressor. 
a. Conduct five steady-state wet coil tests: 
The A 2, EV, B2, B1, and F 1Tests. Use the two dry-coil tests, the steady-state G 1Test and the 
cyclic I 1Test, to determine the cooling mode 
cyclic degradation coefficient, C Dc. Table 7 
specifies test conditions for these seven tests. Determine the intermediate compressor 
speed cited in Table 7 using: 
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 F
1Test. 
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 E
V Test, a cooling-mode intermediate 
compressor speed that falls within 1⁄4and 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 E
VTest 
conditions and bracketed compressor speed range. The manufacturer can designate that one or more indoor units are turned off for the E
VTest. 
TABLE 7—C OOLING MODETESTCONDITION FOR UNITS HAVING A VARIABLE -SPEED COMPRESSOR  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor 
speed Cooling air 
volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
A2Test—required (steady, wet 
coil).80 67 95 175 ................... Maximum ........... Cooling Full- 
Load.2 
B2Test—required (steady, wet 
coil).80 67 82 165 ................... Maximum ........... Cooling Full- 
Load.2 
EVTest—required (steady, wet 
coil).80 67 87 169 ................... Intermediate ...... Cooling Inter-
mediate.3 
B1Test—required (steady, wet 
coil).80 67 82 165 ................... Minimum ............ Cooling Min-
imum.4 
F1Test—required (steady, wet 
coil).80 67 67 153.5 ................ Minimum ............ Cooling Min-
imum.4 
G1Test5—required (steady, dry- 
coil).80 (6) 67 Minimum ........... Cooling Min-
imum4.
I1Test5—required (cyclic, dry-coil) 80 (6) 67 Minimum ........... (6).
1The specified test condition only applies if the unit rejects condensate to the outdoor coil. 
2Defined in section 3.1.4.1. 
3Defined in section 3.1.4.3. 
4Defined in section 3.1.4.2. 
5The 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 °F or less. 
6Maintain 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 G 1Test. 
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, A
2, A1, B, B 2, 
B1, EV, and F 1Tests). 
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 
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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 § 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 Q ˙
ck(T), 
Q˙sck(T) and E ˙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 Q ˙
ck(T) by 
where V ˙sis the average measured indoor air 
volume rate expressed in units of cubic feet 
per minute of standard air (scfm). 
TABLE 8—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR SECTION 3.3 S TEADY -STATE WETCOILCOOLING  
MODETESTS AND SECTION 3.4 D RYCOILCOOLING MODETESTS  
Test operating 
tolerance1 Test condition 
tolerance1 
Indoor dry-bulb, °F ................................................................................................................................................... ........................ ........................
Entering temperature ........................................................................................................... ............................. 2.0 0.5 
Leaving temperature ......................................................................................................................................... 2.0 ........................
Indoor wet-bulb, °F .................................................................................................................................................. ........................ ........................
Entering temperature ........................................................................................................... ............................. 1.0 20.3 
Leaving temperature .........................................................................................................................................21.0 ........................
Outdoor dry-bulb, °F ................................................................................................................................................ ........................ ........................
Entering temperature ........................................................................................................... ............................. 2.0 0.5 
Leaving temperature .........................................................................................................................................32.0 ........................
Outdoor wet-bulb, °F ............................................................................................................................................... ........................ ........................
Entering temperature ........................................................................................................... ............................. 1.0 40.3 
Leaving temperature .........................................................................................................................................31.0 ........................
External resistance to airflow, inches of water ................................................................................ ........................ 0.12 50.02 
Electrical voltage, % of rdg. .................................................................................................. ................................... 2.0 1.5 
Nozzle pressure drop, % of rdg. ............................................................................................................................. 8.0 ........................
1See section 1.2, Definitions. 
2Only applies during wet coil tests; does not apply during steady-state, dry coil cooling mode tests. 
3Only applies when using the Outdoor Air Enthalpy Method. 
4Only applies during wet coil cooling mode tests where the unit rejects condensate to the outdoor coil. 
5Only 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 (DP
min) by 0.03 inches 
of water or more. 
1. Measure the average power consumption 
of the indoor blower motor (E ˙fan,1) and record the corresponding external static pressure 
(DP 1) 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 DP
1+ (DP 1¥ DPmin). 3. After re-establishing steady readings of 
the fan motor power and external static 
pressure, determine average values for the indoor blower power (E ˙
fan,2) and the external 
static pressure (DP 2) by making 
measurements over a 5-minute interval. 
4. Approximate the average power 
consumption of the indoor blower motor at DP
minusing linear extrapolation: 
5. Increase the total space cooling capacity, 
Q˙ck(T), by the quantity (E ˙fan,1¥ E˙fan,min ), 
when expressed on a Btu/h basis. Decrease 
the total electrical power, E ˙ck(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, C 1, C2, and 
G1Tests). 
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 Q ˙
ss,dry and E ˙ss,dry.With regard to a 
section 3.3 deviation, do not adjust Q ˙ss,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 
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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, DT (Set SS) and DT (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: 
Each time a subsequent set of temperature 
differences is recorded (if sampling more 
frequently than every 5 minutes), calculate F
CDusing the most recent seven sets of 
values. Continue these calculations until the 30-minute period is completed or until a value for F
CDis 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 F
CDare within the allowable range, 
save the final value of the ratio from the 30- minute test as F
CD*. 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 F
CD*= 1. 
3.5 Test procedures for the cyclic dry-coil 
cooling-mode tests (the D, D 1, D2, and I 1 
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 (Dt
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 (Dt
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 °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 C
Dfor each complete 
active cycle if the test tolerances given in Table 9 are satisfied. If the average C
Dfor the 
first three active cycles is within 0.02 of the average C Dfor the first two active cycles, use 
the average C Dof the three active cycles as 
the final result. If these averages differ by 
more than 0.02, continue the test to get C D 
for the fourth cycle. If the average C Dof the 
last three cycles is lower than or no more than 0.02 greater than the average C
Dof the 
first three cycles, use the average C Dof all 
four active cycles as the final result. Otherwise, continue the test with a fifth cycle. If the average C
Dof the last three 
cycles is 0.02 higher than the average for the previous three cycles, use the default C
D, 
otherwise use the average C Dof all five active 
cycles. If the test tolerances given in Table 9 are not satisfied, use default C
Dvalue. The 
default C Dvalue 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 Dt
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 
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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—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR CYCLIC DRYCOILCOOLING MODETESTS  
Test operating 
tolerance1 Test condition 
tolerance1 
Indoor entering dry-bulb temperature2, °F .............................................................................................................. 2.0 0.5 
Indoor entering wet-bulb temperature, °F ............................................................................................................... ........................ (3) 
Outdoor entering dry-bulb temperature2, °F ........................................................................................................... 2.0 0.5 
External resistance to airflow2, inches of water ..................................................................................................... 0.12 ........................
Airflow nozzle pressure difference or velocity pressure2, % of reading ................................................................. 8.0 42.0 
Electrical voltage5, % of rdg. .................................................................................................................................. 2.0 1.5 
1See section 1.2, Definitions. 
2Applies 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. 
3Shall at no time exceed a wet-bulb temperature that results in condensate forming on the indoor coil. 
4The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state dry coil test. 
5Applies during the interval when at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are oper-
ating 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 e cyc,dry and 
express it in units of watt-hours. Calculate the total space cooling delivered, q cyc,dry , in 
units of Btu using, 
where vÔ, Cp,a, vn′ (or v n), W n, and F CD* are 
the values recorded during the section 3.4 
dry coil steady-state test and 
Tal(t) = dry bulb temperature of the air 
entering the indoor coil at time t, °F. 
Ta2(t) = dry bulb temperature of the air 
leaving the indoor coil at time t, °F. 
t1= 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. 
t
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 e
cyc,dry by the quantity, 
where VÔ
sis 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 e
cyc,dry and decrease q cyc,dry based on: 
a. The product of [t 2¥t1] 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. 
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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 e
cyc,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, e
cyc,dry. Add the electrical 
energy used by the indoor blower during the 
3 minutes after compressor cutoff to the integrated cooling capacity, q
cyc,dry. For the 
case where the non-ducted unit uses a variable-speed indoor blower which is disabled during the cyclic test, correct e
cyc,dry  
and q cyc,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, 
C
Dc. 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., C
Dc(k=2) = C Dc. Evaluate C Dcusing the above 
results and those from the section 3.4 dry- coil steady-state test. 
the average energy efficiency ratio during the cyclic dry coil cooling mode test, Btu/W·h 
the average energy efficiency ratio during the steady-state dry coil cooling mode test, Btu/ 
W·h 
the cooling load factor dimensionless 
Round the calculated value for C Dcto the 
nearest 0.01. If C Dcis 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, C
Dh. Test conditions 
for the four tests are specified in Table 10. 
TABLE 10—H EATING MODETESTCONDITIONS FOR UNITS HAVING A SINGLE -SPEED COMPRESSOR AND A FIXED-SPEED  
INDOOR BLOWER , ACONSTANT AIRVOLUME RATEINDOOR BLOWER , ORNOINDOOR BLOWER  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°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 
1Defined in section 3.1.4.4. 
2Maintain 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 (H1
2and H1 1), one Frost Accumulation 
Test (H2 2), and two Low Temperature Tests 
(H3 2and H3 1). Conducting an additional 
Frost Accumulation Test (H2 1) is optional. 
Conduct the High Temperature Cyclic (H1C 1) 
Test to determine the heating mode cyclic- degradation coefficient, C
Dh. Test conditions for the seven tests are specified in Table 11. 
If the optional H2 1Test is not performed, use 
the following equations to approximate the capacity and electrical power of the heat pump at the H2
1test conditions: 
where, 
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The quantities Q ˙hk=2(47), E ˙hk=2(47), Q ˙hk=1(47), 
and E ˙hk=1(47) are determined from the H1 2 
and H1 1Tests and evaluated as specified in 
section 3.7; the quantities Q ˙hk=2(35) and E˙hk=2(35) are determined from the H2 2Test 
and evaluated as specified in section 3.9; and 
the quantities Q ˙hk=2(17), E ˙hk=2(17), Q hk=1(17), 
and E ˙hk=1(17), are determined from the H3 2 and H3 1Tests and evaluated as specified in 
section 3.10. 
TABLE 11—H EATING MODETESTCONDITIONS FOR UNITS WITH A SINGLE -SPEED COMPRESSOR THATMEET THE SECTION  
3.6.2 I NDOOR UNITREQUIREMENTS  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Heating air volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
H12Test (required, steady) .................................. 70 60(max) 47 43 Heating Full-load.1 
H11Test (required, steady) .................................. 70 60(max) 47 43 Heating Minimum.2 
H1C 1Test (required, cyclic) ................................. 70 60(max) 47 43 (3) 
H22Test (required) ............................................... 70 60(max) 35 33 Heating Full-load.1 
H21Test (optional) ................................................ 70 60(max) 35 33 Heating Minimum.2 
H32Test (required, steady) .................................. 70 60(max) 17 15 Heating Full-load.1 
H31Test (required, steady) .................................. 70 60(max) 17 15 Heating Minimum.2 
1Defined in section 3.1.4.4. 
2Defined in section 3.1.4.5. 
3Maintain 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 1Test. 
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 (H0
1), two High Temperature Tests 
(H1 2and H1 1), one Frost Accumulation Test 
(H2 2), and one Low Temperature Test (H3 2). Conduct an additional Frost Accumulation 
Test (H2 1) and Low Temperature Test (H3 1) 
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 °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 °F and less. 
If the above two conditions are met, an 
alternative to conducting the H2
1Frost 
Accumulation is to use the following equations to approximate the capacity and electrical power: 
Determine the quantities Q ˙hk=1(47) and 
E˙hk=1(47) from the H1 1Test and evaluate 
them according to Section 3.7. Determine the quantities Q ˙
hk=1(17) and E ˙hk=1(17) from the 
H3 1Test and evaluate them according to 
Section 3.10. b. Conduct the High Temperature Cyclic 
Test (H1C 1) to determine the heating mode 
cyclic-degradation coefficient, C Dh. If a two- 
capacity heat pump locks out low capacity 
operation at lower outdoor temperatures, 
conduct the High Temperature Cyclic Test (H1C
2) to determine the high-capacity heating mode cyclic-degradation coefficient, 
CDh(k=2). The default C Dh(k=2) is the same 
value as determined or assigned for the low- capacity cyclic-degradation coefficient, C
Dh 
[or equivalently, C Dh(k=1)]. Table 12 
specifies test conditions for these nine tests. 
TABLE 12—H EATING MODETESTCONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor 
capacity Heating air 
volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
H01Test (required, steady) ............... 70 60(max) 62 56.5 Low ................ Heating Min-
imum.1 
H12Test (required, steady) ............... 70 60(max) 47 43 High ............... Heating Full- 
Load.2 
H1C 2Test (required,7cyclic) ............. 70 60(max) 47 43 High ............... (3). 
H11Test (required) ............................ 70 60(max) 47 43 Low ................ Heating Min-
imum.1 
H1C 1Test (required, cyclic) .............. 70 60(max) 47 43 Low ................ (4). 
H22Test (required) ............................ 70 60(max) 35 33 High ............... Heating Full- 
Load.2 
H21Test56(required) ........................ 70 60(max) 35 33 Low ................ Heating Min-
imum.1 
H32Test (required, steady) ............... 70 60(max) 17 15 High ............... Heating Full- 
Load.2 
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TABLE 12—H EATING MODETESTCONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR —Continued 
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor 
capacity Heating air 
volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
H31Test5(required, steady) ............. 70 60(max) 17 15 Low ................ Heating Min-
imum.1 
1Defined in section 3.1.4.5. 
2Defined in section 3.1.4.4. 
3Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H1 2Test. 
4Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H1 1Test. 
5Required only if the heat pump’s performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is need-
ed to complete the section 4.2.3 HSPF calculations. 
6If table note #5 applies, the section 3.6.3 equations for Q ˙hk=1(35) and E ˙hk=1(17) may be used in lieu of conducting the H2 1Test. 
7Required 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 (H0 1), two High Temperature Tests (H1 2 
and H1 1), one Frost Accumulation Test 
(H2 V), and one Low Temperature Test (H3 2). Conducting one or both of the following tests 
is optional: An additional High Temperature Test (H1
N) and an additional Frost 
Accumulation Test (H2 2). Conduct the 
Maximum Temperature Cyclic (H0C 1) Test to 
determine the heating mode cyclic- degradation coefficient, C Dh. 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: 
Where a tolerance of plus 5 percent or the 
next higher inverter frequency step from that calculated is allowed. If the H2 2Test is not 
done, use the following equations to approximate the capacity and electrical power at the H2
2test conditions: 
b. Determine the quantities Q ˙hk=2(47) and 
from E ˙hk=2(47) from the H1 2Test and 
evaluate them according to section 3.7. 
Determine the quantities Q ˙hk=2(17) and 
E˙hk=2(17) from the H3 2Test 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 H1
NTest if the manufacturer requests it. If 
the H1 NTest is done, operate the heat 
pump’s compressor at the same speed as the speed used for the cooling mode A 2Test. 
Refer to the last sentence of section 4.2 to see 
how the results of the H1 NTest may be used 
in calculating the heating seasonal performance factor. 
TABLE 13—H EATING MODETESTCONDITIONS FOR UNITS HAVING A VARIABLE -SPEED COMPRESSOR  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor 
speed Heating air 
volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
H01Test (required, steady) ............... 70 60(max) 62 56.5 Minimum ........ Heating Min-
imum.1 
H0C 1Test (required, steady) ............. 70 60(max) 62 56.5 Minimum ........ (2). 
H12Test (required, steady) ............... 70 60(max) 47 43 Maximum ....... Heating Full- 
Load.3 
H11Test (required, steady) ............... 70 60(max) 47 43 Minimum ........ Heating Min-
imum.1 
H1NTest (optional, steady) ............... 70 60(max) 47 43 Cooling Mode 
Maximum.Heating Nominal.4 
H22Test (optional) ............................. 70 60(max) 35 33 Maximum ....... Heating Full- 
Load.3 
H2VTest (required) ........................... 70 60(max) 35 33 Intermediate ... Heating Inter-
mediate.5 
H32Test (required, steady) ............... 70 60(max) 17 15 Maximum ....... Heating Full- 
Load.3 
1Defined in section 3.1.4.5. 
2Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as meas-
ured during the H0 1Test. 
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3Defined in section 3.1.4.4. 
4Defined in section 3.1.4.7. 
5Defined 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 H2
V 
Test, a heating mode intermediate compressor speed that falls within 
1⁄4and 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 H2
VTest 
conditions and bracketed compressor speed range. The manufacturer can designate that one or more specific indoor units are turned off for the H2
VTest. 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 
(H0
1), two high-temperature tests (H1 2and H1 1), one Frost Accumulation test (H2 2), two 
low-temperature tests (H3 2, H3 3), and one 
minimum-temperature test (H4 3). Conduct an 
additional Frost Accumulation test (H2 1) and 
low- temperature test (H3 1) 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 °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 °F 
and less. If the above two conditions are met, an alternative to conducting the H2
1Frost 
Accumulation Test to determine Q ˙hk=1(35) 
and E ˙hk=1(35) is to use the following 
equations to approximate this capacity and electrical power: 
In evaluating the above equations, 
determine the quantities Q ˙hk=1(47) from the 
H1 1Test and evaluate them according to 
section 3.7. Determine the quantities 
Q˙hk=1(17) and E ˙hk=1(17) from the H3 1Test 
and evaluate them according to section 3.10. Use the paired values of Q ˙
hk=1(35) and E˙hk=1(35) derived from conducting the H2 1 
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 
(H2
3) with the heat pump operating at its 
booster capacity is optional. If this optional 
test is not conducted, determine Q hk=3(35) 
and E hk=3(35) using the following equations 
to approximate this capacity and electrical power: 
where: 
Determine the quantities Q ˙hk=2(47) and 
E˙hk=2(47) from the H1 2Test and evaluate 
them according to section 3.7. Determine the 
quantities Q ˙hk=2(35) and E ˙hk=2(35) from the 
H2 2Test and evaluate them according to 
section 3.9.1. Determine the quantities 
Q˙hk=2(17) and E ˙hk=2(17) from the H3 2Test, 
determine the quantities Q ˙hk=3(17) and 
E˙hk=3(17) from the H3 3Test, and determine 
the quantities Q ˙hk=3(2) and E ˙hk=3(2) from the 
H4 3Test. Evaluate all six quantities according 
to section 3.10. Use the paired values of Q˙hk=3(35) and E ˙hk=3(35) derived from 
conducting the H2 3Frost 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 (H1C
1) to determine the heating mode 
cyclic-degradation coefficient, C Dh. If a triple- 
capacity heat pump locks out low capacity operation at lower outdoor temperatures, conduct the high-temperature cyclic test 
(H1C
2) to determine the high-capacity 
heating mode cyclic-degradation coefficient, C
Dh(k=2). The default C Dh(k=2) is the same 
value as determined or assigned for the low- 
capacity cyclic-degradation coefficient, C Dh 
[or equivalently, C Dh(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 (H3C
3) to determine 
the booster-capacity heating mode cyclic- 
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degradation coefficient, C Dh(k=3). The 
default C Dh(k=3) is the same value as determined or assigned for the high-capacity 
cyclic-degradation coefficient, C Dh[or equivalently, C Dh(k=2)]. Table 14 specifies 
test conditions for all 13 tests. 
TABLE 14—H EATING MODETESTCONDITIONS FOR UNITS WITH A TRIPLE -CAPACITY COMPRESSOR  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor 
capacity Heating air vol-
ume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
H01Test (required, steady) ............... 70 60(max) 62 56.5 Low ................ Heating Min-
imum.1 
H12Test (required, steady) ............... 70 60(max) 47 43 High ............... Heating Full- 
Load.2 
H1C 2Test (required,8cyclic) ............. 70 60(max) 47 43 High ...............3. 
H11Test (required) ............................ 70 60(max) 47 43 Low ................ Heating Min-
imum1. 
H1C 1Test (required, cyclic) .............. 70 60(max) 47 43 Low ................4. 
H23Test (optional, steady) ................ 70 60(max) 35 33 Booster .......... Heating Full- 
Load.2 
H22Test (required) ............................ 70 60(max) 35 33 High ............... Heating Full- 
Load.2 
H21Test (required) ............................ 70 60(max) 35 33 Low ................ Heating Min-
imum.1 
H33Test (required, steady) ............... 70 60(max) 17 15 Booster .......... Heating Full- 
Load.2 
H3C 3Test56(required, cyclic) .......... 70 60(max) 17 15 Booster ..........7. 
H32Test (required, steady) ............... 70 60(max) 17 15 High ............... Heating Full- 
Load.2 
H31Test5(required, steady) ............. 70 60(max) 17 15 Low ................ Heating Min-
imum.1 
H43Test (required, steady) ............... 70 60(max) 2 1 Booster .......... Heating Full- 
Load.2 
1Defined in section 3.1.4.5. 
2Defined in section 3.1.4.4. 
3Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H1 2Test. 
4Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H1 1Test. 
5Required only if the heat pump’s performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is need-
ed to complete the section 4.2.6 HSPF calculations. 
6If table note 5applies, the section 3.6.6 equations for Q ˙hk=1(35) and E ˙hk=1(17) may be used in lieu of conducting the H2 1Test. 
7Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H3 3Test. 
8Required 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 H0
1, H1, 
H1 2, H1 1, and H1 NTests). 
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 § 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—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR SECTION 3.7 ANDSECTION 3.10 S TEADY -STATE 
HEATING MODETESTS  
Test 
operating 
tolerance1 Test 
condition 
tolerance1 
Indoor dry-bulb, °F: 
Entering temperature ........................................................................................................... ............................. 2 .0 0 .5 
Leaving temperature ......................................................................................................................................... 2 .0 ........................
Indoor wet-bulb, °F: 
Entering temperature ........................................................................................................... ............................. 1 .0 ........................
Leaving temperature ......................................................................................................................................... 1 .0 ........................
Outdoor dry-bulb, °F: 
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TABLE 15—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR SECTION 3.7 ANDSECTION 3.10 S TEADY -STATE 
HEATING MODETESTS —Continued 
Test 
operating 
tolerance1 Test 
condition 
tolerance1 
Entering temperature ........................................................................................................... ............................. 2 .0 0 .5 
Leaving temperature .........................................................................................................................................22 .0 ........................
Outdoor wet-bulb, °F: 
Entering temperature ........................................................................................................... ............................. 1 .0 0 .3 
Leaving temperature .........................................................................................................................................21 .0 ........................
External resistance to airflow, inches of water ................................................................................ ........................ 0 .12 30 .02 
Electrical voltage, % of rdg ................................................................................................... ........................... 2 .0 1 .5 
Nozzle pressure drop, % of rdg ................................................................................................. ...................... 8 .0 ........................
1See section 1.2, Definitions. 
2Only applies when the Outdoor Air Enthalpy Method is used. 
3Only 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 § 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 Q ˙
hkand E ˙hk(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 H1
NTest, if 
conducted. 
c. For heat pumps tested without an indoor 
blower installed, increase Q ˙hk(T) by 
where VÔ
sis 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 °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 Q ˙
hk(47) and E ˙hk(47). 
d. If conducting the cyclic heating mode 
test, which is described in section 3.8, record the average indoor-side air volume rate, VÔ, 
specific heat of the air, C
p,a(expressed on dry 
air basis), specific volume of the air at the nozzles, v
n′ (or v n), humidity ratio at the 
nozzles, W n, 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 (E ˙
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 (DP
1) exceeds the 
applicable section 3.1.4.4 minimum (or targeted) external static pressure (DP
min) by 
0.03 inches of water or more. 
Determine E ˙fan,1by 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 E ˙
fan,1 
(which corresponds to DP 1): 
i. While maintaining the same test 
conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately DP
1+ (DP 1¥ DPmin). 
ii. After re-establishing steady readings for 
fan motor power and external static pressure, determine average values for the indoor blower power (E ˙
fan,2) and the external static 
pressure (DP 2) 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 DP
minusing linear extrapolation: 
iv. Decrease the total space heating 
capacity, Q ˙hk(T), by the quantity (E ˙fan,1¥ 
E˙fan,min ), when expressed on a Btu/h basis. 
Decrease the total electrical power, E ˙hk(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, DT (Set SS) and DT (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: 
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Each time a subsequent set of temperature 
differences is recorded (if sampling more 
frequently than every 5 minutes), calculate F
CDusing the most recent seven sets of 
values. Continue these calculations until the 30-minute period is completed or until a value for F
CDis 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 F
CDare within the allowable range, 
save the final value of the ratio from the 30- minute test as F
CD*. 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 F
CD*= 1. 
3.8 Test procedures for the cyclic heating 
mode tests (the H0C 1, H1C, H1C 1and H1C 2 
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 C
Dvalue 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, q
cyc, as specified in section 3.5 
except for making the following changes: 
(1) When evaluating Equation 3.5–1, use 
the values of VÔ, Cp,a,vn′, (or v n), and W nthat 
were recorded during the section 3.7 steady- state test conducted at the same test conditions. 
(2) Calculate G using, 
where F CD* 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 q
cycby the 
amount calculated using Equation 3.5–3. Additionally, increase e
cycby the amount 
calculated using Equation 3.5–2. In making these calculations, use the average indoor air volume rate (VÔ
s) 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, q
cyc. 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 q
cycand e cyc. 
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 C
Dh. 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 § 430.3) in determining Q˙
hk(Tcyc) (or q cyc). The default value for two- 
capacity units cycling at high capacity, however, is the low-capacity coefficient, i.e., C
Dh(k=2) = C Dh. The tested C Dhis calculated 
as follows: 
Where, 
the average coefficient of performance during 
the cyclic heating mode test, 
dimensionless. 
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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. 
the heating load factor, dimensionless. T
cyc= the nominal outdoor temperature at 
which the cyclic heating mode test is conducted, 62 or 47 °F. Dt
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 C
Dhto the 
nearest 0.01. If C Dhis negative, then set it 
equal to zero. 
TABLE 16—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR CYCLIC HEATING MODETESTS  
Test 
operating 
tolerance1 Test 
condition 
tolerance1 
Indoor entering dry-bulb temperature,2°F .............................................................................................................. 2.0 0.5 
Indoor entering wet-bulb temperature,2°F .............................................................................................................. 1.0 ............ ............
Outdoor entering dry-bulb temperature,2°F ............................................................................................................ 2.0 0.5 
Outdoor entering wet-bulb temperature,2°F ........................................................................................................... 2.0 1.0 
External resistance to air-flow,2inches of water ..................................................................................................... 0.12 ........................
Airflow nozzle pressure difference or velocity pressure,2% of reading .................................................................. 2.0 32.0 
Electrical voltage,4% of rdg ..................................................................................................................................... 8.0 1.5 
1See section 1.2, Definitions. 
2Applies 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. 
3The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state test conducted at 
the same test conditions. 
4Applies during the interval that at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are oper-
ating, except for the first 30 seconds after compressor start-up. 
3.9 Test procedures for Frost 
Accumulation heating mode tests (the H2, 
H2 2, H2 V, and H2 1Tests). 
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, Dt
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 Q
mishould read:) 
Record the electrical energy consumed, expressed in watt-hours, from defrost termination to defrost termination, e
DEFk(35), 
as well as the corresponding elapsed time in hours, Dt
FR. 
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TABLE 17—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR FROST ACCUMULATION HEATING MODETESTS  
Test operating tolerance1 Test condition 
tolerance1 
Sub-interval H2 Sub-interval H2 Sub-interval D3 
Indoor entering dry-bulb temperature, °F .................................................................... 2 .0 44.0 0 .5 
Indoor entering wet-bulb temperature, °F ................................................................... 1 .0 
Outdoor entering dry-bulb temperature, °F ................................................................. 2 .0 10.0 1 .0 
Outdoor entering wet-bulb temperature, °F ................................................................. 1 .5 0 .5 
External resistance to airflow, inches of water ............................................................ 0 .12 50 .02 
Electrical voltage, % of rdg .......................................................................................... 2 .0 1 .5 
1See section 1.2, Definitions. 
2Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a defrost cycle. 
3Applies 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. 
4For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies during the 10 minute interval that fol-
lows defrost termination. 
5Only applies when testing non-ducted heat pumps. 
3.9.1 Average space heating capacity and 
electrical power calculations. a. Evaluate average space heating capacity, 
Q˙hk(35), when expressed in units of Btu per 
hour, using: 
Where, 
VÔ= the average indoor air volume rate 
measured during Sub-interval H, cfm. 
Cp,a= 0.24 + 0.444 · W n, 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/lbm da· °F. 
vn′ = specific volume of the air-water vapor 
mixture at the nozzle, ft3/lbmmx. Wn= humidity ratio of the air-water vapor 
mixture at the nozzle, lbm of water vapor per lbm of dry air. 
Dt
FR= t2¥ t1, the elapsed time from defrost 
termination to defrost termination, hr. 
Tal(t) = dry bulb temperature of the air 
entering the indoor coil at elapsed time 
t, °F; only recorded when indoor coil 
airflow occurs; assigned the value of zero during periods (if any) where the indoor blower cycles off. 
T
a2(t) = dry bulb temperature of the air 
leaving the indoor coil at elapsed time t, 
°F; only recorded when indoor coil airflow occurs; assigned the value of zero during periods (if any) where the indoor blower cycles off. t
1= the elapsed time when the defrost 
termination occurs that begins the 
official test period, hr. 
t2= the elapsed time when the next 
automatically occurring defrost termination occurs, thus ending the official test period, hr. 
v
n= 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
3per 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 Q ˙
hk(35) in accordance with section 
7.3.4.3 of ASHRAE Standard 37–2009 (incorporated by reference, see § 430.3). 
b. Evaluate average electrical power, 
E˙
hk(35), when expressed in units of watts, 
using: 
For heat pumps tested without an indoor 
blower installed, increase QÇ
hk(35) by, 
and increase E ˙hk(35) by, 
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Where VÔ
sis 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 (DP
min) by 0.03 inches of water or 
more: 1. Measure the average power consumption 
of the indoor blower motor (E ˙fan,1) and record 
the corresponding external static pressure 
(DP 1) 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 DP
1+ (DP 1¥ 
DPmin). 
3. After re-establishing steady readings for 
the fan motor power and external static 
pressure, determine average values for the indoor blower power (E ˙
fan,2) and the external 
static pressure (DP 2) 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 DP
minusing linear 
extrapolation: 
5. Decrease the total heating capacity, 
Q˙hk(35), by the quantity [(E ˙fan,1¥E˙fan,min )· (Dt 
a/Dt FR], when expressed on a Btu/h basis. 
Decrease the total electrical power, E hk(35), by the same quantity, now expressed in 
watts. 
3.9.2 Demand defrost credit. a. Assign the demand defrost credit, F
def, 
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 F
defusing, 
Where, 
Dtdef= the time between defrost terminations 
(in hours) or 1.5, whichever is greater. A 
value of 6 must be assigned to Dt defif 
this limit is reached during a Frost 
Accumulation test and the heat pump has not completed a defrost cycle. 
Dt
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 Dt
defthat 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 Dt
defbased 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, H3
2, 
and H3 1Tests). 
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 Q ˙
hk(17) and E ˙hk(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 Q ˙
hk(17) 
and E ˙hk(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 °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 
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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 § 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 °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 § 430.3); sections 5, 6, 7, 8, 9, and 11 of ASHRAE Standard 41.9–2011 (incorporated by reference, see § 430.3); and section 7.4 of ASHRAE Standard 37– 2009(incorporated by reference, see § 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 § 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, B
1, or B 2Test, 
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 P1
x: 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 P1
x, the 
shoulder season total off mode power. 
c. Measure P xfor 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, P
x. 
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 (P1
x) 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: 
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 (P
x) from the shoulder season 
total off mode power (P1 x) 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: 
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 °F per hour and achieve an outdoor dry-bulb temperature of 72 °F. Maintain this temperature within ±2 °F 
for at least 5 minutes, while maintaining an indoor dry-bulb temperature of between 75 °F and 85 °F. 
b. Measure P1
x: 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 P1
x, 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 °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 °F for at least 5 
minutes, while maintaining an indoor dry- bulb temperature of between 75 °F and 85 °F. 
d. Measure P2
x: 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 P2
x, the heating 
season total off mode power. 
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e. Measure P xfor 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, P
x. 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 (P1
x) 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: 
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 (P
x) from the shoulder season 
total off mode power (P1 x) 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: 
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 (P2 x) 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: 
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 (P
x) from the heating season 
total off mode power (P2 x) 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: 
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, 
Where, 
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Tj= the outdoor bin temperature, °F. Outdoor 
temperatures are grouped or ‘‘binned.’’ 
Use bins of 5 °F with the 8 cooling season bin temperatures being 67, 72, 77, 
82, 87, 92, 97, and 102 °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(T j). 
When referenced, evaluate BL(T j) for cooling 
using, 
where, 
Q˙ck=2(95) = the space cooling capacity 
determined from the A 2Test and 
calculated as specified in section 3.3, 
Btu/h. 
1.1 = sizing factor, dimensionless. The temperatures 95 °F and 65 °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) * EER
B 
where, 
PLF(0.5) = 1 ¥ 0.5 · C Dc, 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 Q ˙c(82) and 
E˙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 °F to 102 °F. Calculate SEER using Equation 4.1–1. Evaluate the quantity q
c(Tj)/N in Equation 
4.1–1 using, 
where, 
Q˙c(Tj) = the space cooling capacity of the test 
unit when operating at outdoor 
temperature, T j, 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 T
j 
to the total number of hours in the cooling season, dimensionless. a. For the space cooling season, assign n
j/ 
N as specified in Table 18. Use Equation 4.1– 
2 to calculate the building load, BL(T j). 
Evaluate Q ˙c(Tj) using, 
the space cooling capacity of the test unit at 
outdoor temperature T jif operated at the 
Cooling Minimum Air Volume Rate, Btu/h. 
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the space cooling capacity of the test unit at 
outdoor temperature T jif operated at the 
Cooling Full-load Air Volume Rate, Btu/h. 
b. For units where indoor blower speed is 
the primary control variable, FP ck=1denotes 
the fan speed used during the required A 1 
and B 1Tests (see section 3.2.2.1), FP ck=2 denotes the fan speed used during the required A
2and B 2Tests, and FP c(Tj) denotes 
the fan speed used by the unit when the outdoor temperature equals T
j.For units 
where indoor air volume rate is the primary 
control variable, the three FP c’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 Q˙
ck=1(82), Q ˙ck=1(95),Q ˙ck=2(82), and 
Q˙ck=2(95). 
where, 
PLF j= 1 ¥ CDc· [1 ¥ X(T j)], the part load 
factor, dimensionless. E˙c(Tj) = the electrical power consumption of 
the test unit when operating at outdoor 
temperature T j, W. c. The quantities X(T j) and n j/N are the 
same quantities as used in Equation 4.1.2–1. 
d. Evaluate E ˙c(Tj) using, 
the electrical power consumption of the test 
unit at outdoor temperature T jif operated at 
the Cooling Minimum Air Volume Rate, W. 
e. The parameters FP ck=1, and FP ck=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 E˙
ck=1(82), E ˙ck=1(95), E ˙ck=2(82), and E ˙ck=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, Q ˙
ck=1(Tj), and electrical power 
consumption, E ˙ck=1(Tj), of the test unit when 
operating at low compressor capacity and outdoor temperature T
jusing, 
where Q ˙ck=1(82) and E ˙ck=1(82) are 
determined from the B 1Test, Q ˙ck=1(67) and 
E˙ck=1(67) are determined from the F 1Test, and all four quantities are calculated as 
specified in section 3.3. Evaluate the space cooling capacity, Q ˙
ck=2(Tj), and electrical power consumption, E ˙ck=2(Tj), of the test 
unit when operating at high compressor capacity and outdoor temperature T
jusing, 
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where Q ˙ck=2(95) and E ˙ck=2(95) are determined 
from the A 2Test, Q ˙ck=2(82), and E ˙ck=2(82), are 
determined from the B 2Test, and all are 
calculated as specified in section 3.3. 
The calculation of Equation 4.1–1 
quantities q c(Tj)/N and e c(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(T
j), 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 T
j, Q˙ck=1(Tj) ≥ BL(T j). 
where, Xk=1(Tj) = BL(T j)/Q˙ck=1(Tj), the cooling mode 
low capacity load factor for temperature 
bin j, dimensionless. PLF j= 1 ¥ CDc· [1 ¥ Xk=1(Tj)], the part load 
factor, dimensionless. 
Obtain the fractional bin hours for the 
cooling season, n j/N, from Table 18. Use Equations 4.1.3–1 and 4.1.3–2, respectively, to evaluate Q ˙
ck=1(Tj) and E ˙ck=1(Tj). 
TABLE 18—D ISTRIBUTION OF FRACTIONAL HOURS WITHIN COOLING SEASON TEMPERATURE BINS 
Bin number, j Bin temperature 
range °F Representative 
temperature for 
bin °F Fraction of total 
temperature bin 
hours, n j/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 T j, 
Q˙ck=1(Tj) <BL(T j) <Q˙ck=2(Tj). 
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where, 
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, n j/N, from Table 18. Use Equations 4.1.3–1 and 4.1.3–2, respectively, 
to evaluate Q ˙ck=1(Tj) and E ˙ck=1(Tj). Use 
Equations 4.1.3–3 and 4.1.3–4, respectively, 
to evaluate Q ˙ck=2(Tj) and E ˙ck=2(Tj). 
4.1.3.3 Unit only operates at high (k=2) 
compressor capacity at temperature T jand its capacity is greater than the building cooling 
load, BL(T j) < Q ck=2(Tj). This section applies 
to units that lock out low compressor capacity operation at higher outdoor temperatures. 
where, Xk=2(Tj) = BL(T j)/Q˙ck=2(Tj), the cooling mode 
high capacity load factor for temperature 
bin j, dimensionless. PLF j= 1 ¥ CDc(k = 2) * [1 ¥ Xk=2(Tj) the part 
load factor, dimensionless. 
4.1.3.4 Unit must operate continuously at 
high (k=2) compressor capacity at 
temperature T j, BL(T j) ≥ Q˙ck=2(Tj). 
Obtain the fractional bin hours for the 
cooling season, n j/N, from Table 18. Use 
Equations 4.1.3–3 and 4.1.3–4, respectively, 
to evaluate Q ˙ck=2(Tj) and E ˙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, Q ˙
ck=1(Tj), and electrical power 
consumption, E ˙ck=1(Tj), of the test unit when 
operating at minimum compressor speed and outdoor temperature T
j.Use, 
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where Q ˙ck=1(82) and E ˙ck=1(82) are determined 
from the B 1Test, Q ˙ck=1(67) and E ˙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, Q ˙
ck=2(Tj), and electrical power 
consumption, E ˙ck=2(Tj), of the test unit when operating at maximum compressor speed and 
outdoor temperature T j.Use Equations 4.1.3– 
3 and 4.1.3–4, respectively, where Q ˙ck=2(95) 
and E ˙ck=2(95) are determined from the A 2 
Test, Q ˙ck=2(82) and E ˙ck=2(82) are determined 
from the B 2Test, and all four quantities are 
calculated as specified in section 3.3. Calculate the space cooling capacity, 
Q˙ck=v(Tj), and electrical power consumption, 
E˙ck=v(Tj), of the test unit when operating at 
outdoor temperature T jand the intermediate 
compressor speed used during the section 3.2.4 (and Table 7) E
VTest using, 
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 T j, 
Q˙ck=1(Tj) ≥ BL(T j). 
where, 
Xk=1(Tj) = BL(T j)/Q˙ck=1(Tj), the cooling mode 
minimum speed load factor for 
temperature bin j, dimensionless. 
PLF j= 1 ¥ CDc·˙[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 T
j 
to the total number of hours in the cooling season, dimensionless. 
Obtain the fractional bin hours for the 
cooling season, n
j/N, from Table 18. Use Equations 4.1.3–1 and 4.1.3–2, respectively, to evaluate Q ˙
ck=1(Tj) and E ˙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 T
j,Q˙ck=1(Tj) < BL(T j) < Q˙ck=2(Tj). 
where, Q ˙ck=i(Tj) = BL(T j), the space cooling capacity 
delivered by the unit in matching the 
building load at temperature T j, Btu/h. The matching occurs with the unit 
operating at compressor speed k = i. 
the electrical power input required by the test unit when operating at a compressor speed of k = i and temperature T
j, 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 T
j, Btu/h per W. 
Obtain the fractional bin hours for the 
cooling season, n j/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 · T j+ C · T j2. 
For each unit, determine the coefficients A, 
B, and C by conducting the following calculations once: 
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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 (Q ˙
ck=1(Tl) = BL(T 1)), °F. 
Determine T 1by 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 E
VTest, provides a space 
cooling capacity that is equal to the building load (Q ˙
ck=v(Tv) = BL(T v)), °F. 
Determine T vby 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 (Q ˙
ck=2(T2) = BL(T 2)), °F. 
Determine T 2by equating Equations 
4.1.3–3 and 4.1–2 and solving for outdoor temperature. 
4.1.4.3 Unit must operate continuously at 
maximum (k=2) compressor speed at temperature Tj, BL(T j) ≥Q˙ck=2(Tj). Evaluate 
the Equation 4.1–1 quantities 
as specified in section 4.1.3.4 with the 
understanding that Q ˙ck=2(Tj) and E ˙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 q
c(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, Q˙
k=1(Tj), and electrical power consumption, 
E˙k=1(Tj), of the test unit when operating at the 
cooling minimum air volume rate and outdoor temperature T
jusing the equations 
given in section 4.1.2.1. Calculate the space cooling capacity, Q ˙
k=2(Tj), and electrical 
power consumption, E ˙k=2(Tj), of the test unit when operating at the cooling full-load air volume rate and outdoor temperature T
j 
using the equations given in section 4.1.2.1. In evaluating the section 4.1.2.1 equations, determine the quantities Q ˙
k=1(82) and 
E˙k=1(82) from the B1 Test, Q ˙k=1(95) and 
E˙k=1(82) from the Al Test, Q ˙k=2(82) and 
E˙k=2(82) from the B2 Test, and Q ˙k=2(95) and 
E˙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, CD
c, as per sections 
3.2.2.1 and 3.5 to 3.5.3. Assign this same value to CD
c(K=2). c. Except for using the 
above values of Q ˙k=1(Tj), E ˙k=1(Tj), E ˙k=2(Tj), 
Q˙k=2(Tj), CD c, and CD c(K=2), calculate the 
quantities q c(Tj)/N and e c(Tj)/N as specified 
in section 4.1.3.1 for cases where Q ˙k=1(Tj) ≥ 
BL(T j). For all other outdoor bin temperatures, T j, calculate q c(Tj)/N and 
ec(Tj)/N as specified in section 4.1.3.3 if 
Q˙k=2(Tj) > BL (T j) or as specified in section 
4.1.3.4 if Q ˙k=2(Tj) ≤ BL(T j). 
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 q
c(Tj)/ 
N and e c(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, 
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 T
j 
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(T
j)/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 T
jto 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 
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heaters at a particular bin temperature 
may be reflected in e h(Tj)/N (see 4.2.5). 
Tj= the outdoor bin temperature, °F. Outdoor 
temperatures are ‘‘binned’’ such that calculations are only performed based 
one temperature within the bin. Bins of 5 °F are used. 
n
j/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 T
j 
to the total number of hours in the 
heating season, dimensionless. Obtain n
j/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. 
F
def= the demand defrost credit described in 
section 3.9.2, dimensionless. 
BL(T j) = the building space conditioning load 
corresponding to an outdoor temperature of T
j; 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—G ENERALIZED CLIMATIC REGION INFORMATION  
Region Number I II III IV V VI 
Heating Load Hours, HLH ....................... 750 1250 1750 2250 2750 * 2750 
Outdoor Design Temperature, T OD.......... 37 27 17 5 ¥10 30 
j Tj(°F) ..................................................... Fractional Bin Hours, n j/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 
Where, 
TOD= the outdoor design temperature, °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: 
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Where Q ˙hk(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, Q ˙hk(47) = Q ˙h(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, Q˙
nk(47) = Q ˙nk=2(47), the space heating 
capacity determined from the H1 2Test. 
3. For two-capacity, northern heat pumps 
(see section 1.2, Definitions), Q ˙kh(47) = 
Q˙k=1h(47), the space heating capacity 
determined from the H1 1Test. 
If the optional H1 NTest is conducted on 
a variable-speed heat pump, the 
manufacturer has the option of defining Q˙
kh(47) as specified above in item 2 or as Q˙kh(47)=Q ˙k=Nh(47), the space heating 
capacity determined from the H1 NTest. 
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—S TANDARDIZED 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. 
where, 
whichever is less; the heating mode load factor for temperature bin j, dimensionless. Q˙
h(Tj) = the space heating capacity of the 
heat pump when operating at outdoor temperature T
j, Btu/h. E˙h(Tj) = the electrical power consumption of 
the heat pump when operating at 
outdoor temperature T j, W. 
d(T j) = the heat pump low temperature cut- 
out factor, dimensionless. 
PLF j= 1 ¥ C˙Dh· [1 ¥X(T j)] the part load 
factor, dimensionless. Use Equation 4.2–2 to determine BL(T j). 
Obtain fractional bin hours for the heating 
season, n j/N, from Table 19. 
Determine the low temperature cut-out 
factor using 
where, 
Toff= the outdoor temperature when the 
compressor is automatically shut off, °F. (If no such temperature exists, T jis 
always greater than T offand T on). 
Ton= the outdoor temperature when the 
compressor is automatically turned back on, if applicable, following an automatic 
shut-off, °F. 
Calculate Q ˙h(Tj) and E ˙h(Tj) using, 
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where Q ˙h(47) and E ˙h(47) are determined from 
the H1 Test and calculated as specified in 
section 3.7; Q ˙h(35) and E ˙h(35) are determined 
from the H2 Test and calculated as specified in section 3.9.1; and Q ˙
h(17) and E ˙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°F to ¥23°F. Calculate the quantities 
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 H1C 1Test and section 3.6.2. In 
addition, evaluate the space heating capacity and electrical power consumption of the heat 
pump Q ˙h(Tj) and E ˙h(Tj) using 
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 
For units where indoor blower speed is the 
primary control variable, FP hk=1denotes the 
fan speed used during the required H1 1and 
H3 1Tests (see Table 11), FP hk=2denotes the 
fan speed used during the required H1 2, H2 2, 
and H3 2Tests, and FP h(Tj) denotes the fan 
speed used by the unit when the outdoor temperature equals T
j.For units where indoor 
air volume rate is the primary control variable, the three FP h’s are similarly defined 
only now being expressed in terms of air 
volume rates rather than fan speeds. 
Determine Q ˙hk=1(47) and E ˙hk=1(47) from the 
H1 1Test, and Q ˙hk=2(47) and E ˙hk=2(47) from 
the H1 2Test. Calculate all four quantities as 
specified in section 3.7. Determine Q ˙hk=1(35) 
and E ˙hk=1(35) as specified in section 3.6.2; 
determine Q ˙hk=2(35) and E ˙hk=2(35) and from the H2 2Test and the calculation specified in 
section 3.9. Determine Q ˙hk=1(17) and E ˙hk=1(17 
from the H3 1Test, and Q ˙hk=2(17) and 
E˙hk=2(17) from the H3 2Test. 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 
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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. 
a. Evaluate the space heating capacity and 
electrical power consumption of the heat pump when operating at low compressor 
capacity and outdoor temperature T jusing 
b. Evaluate the space heating capacity and 
electrical power consumption (Q ˙hk=2(Tj) and 
E˙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 Q˙
hk=1(62) and E ˙hk=1(62) from the H0 1Test, 
Q˙hk=1(47) and E ˙hk=1(47) from the H1 1Test, 
and Q ˙hk=2(47) and E ˙hk=2(47) from the H1 2 Test. Calculate all six quantities as specified in section 3.7. Determine Q ˙
hk=2(35) and 
E˙hk=2(35) from the H2 2Test and, if required 
as described in section 3.6.3, determine Q˙
hk=1(35) and E ˙hk=1(35) from the H2 1Test. 
Calculate the required 35°F quantities as specified in section 3.9. Determine Q ˙
hk=2(17) 
and E ˙hk=2(17) from the H3 2Test and, if 
required as described in section 3.6.3, determine Q ˙hk=1(17) and E ˙hk=1(17) from the 
H3 1Test. Calculate the required 17 °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 T
j, 
Q˙hk=1(Tj) ≥BL(T j). 
Where, 
Xk=1(Tj) = BL(T j) / Q˙hk=1(Tj), the heating mode 
low capacity load factor for temperature 
bin j, dimensionless. PLF j= 1¥C Dh· [ 1¥Xk=1(Tj)], the part load 
factor, dimensionless. 
d′(T j) = the low temperature cutoff factor, 
dimensionless. Determine the low temperature cut-out 
factor using 
Where T offand T onare 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) T jis 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 
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at a temperature T j, Q˙hk=1(Tj) <BL(T j) 
<Q˙hk=2(Tj). 
Where, 
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, d′(T j), using Equation 4.2.3–3. 
4.2.3.3 Heat pump only operates at high 
(k=2) compressor capacity at temperature T j 
and its capacity is greater than the building heating load, BL(T j) <Q˙hk=2(Tj). This section 
applies to units that lock out low compressor 
capacity operation at low outdoor temperatures. 
Where, 
Xk=2(Tj) = BL(T j)/Q˙hk=2(Tj). PLF j= 1¥C Dh(k 
= 2) * [1¥Xk=2(Tj) If the H1C 2Test described in section 3.6.3 
and Table 12 is not conducted, set C Dh(k=2) 
equal to the default value specified in section 3.8.1. Determine the low temperature cut-out 
factor, d(T
j), using Equation 4.2.3–3. 
4.2.3.4 Heat pump must operate 
continuously at high (k=2) compressor 
capacity at temperature T j, BL(T j) ≥ Q˙hk=2(Tj). 
Where 
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, Q˙
hk=1(Tj), and electrical power consumption, 
E˙hk=1(Tj), of the heat pump when operating at minimum compressor speed and outdoor 
temperature T jusing 
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Where Q ˙hk=1(62) and E ˙hk=1(62) are determined 
from the H0 1Test, Q ˙hk=1(47) and 
E˙hk=1(47) are determined from the 
H1 1Test, and all four quantities are 
calculated as specified in section 3.7. 
Evaluate the space heating capacity, 
Q˙hk=2(Tj), and electrical power 
consumption, E ˙hk=2(Tj), of the heat pump 
when operating at maximum compressor speed and outdoor temperature T
jby 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 Q˙
hk=2(47) and E ˙hk=2(47) from the H1 2Test 
and the calculations specified in section 3.7. Determine Q ˙
hk=2(35) and E ˙hk=2(35) 
from the H2 2Test and the calculations 
specified in section 3.9 or, if the H2 2Test 
is not conducted, by conducting the 
calculations specified in section 3.6.4. Determine Q ˙hk=2(17) and E ˙hk=2(17) from 
the H3 2Test and the calculations 
specified in section 3.10. Calculate the 
space heating capacity, Q ˙hk=v(Tj), and 
electrical power consumption, E ˙hk=v(Tj), 
of the heat pump when operating at outdoor temperature T
jand the 
intermediate compressor speed used during the section 3.6.4 H2
VTest using 
Where Q ˙hk=v(35) and E ˙hk=v(35) are determined 
from the H2 VTest and calculated as specified in section 3.9. Approximate the 
slopes of the k=v intermediate speed heating capacity and electrical power input curves, M
Qand M E, as follows: 
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 T
j, Q˙hk=1(Tj≥ BL(T j). Evaluate the Equation 4.2– 
1 quantities 
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as specified in section 4.2.3.1. Except now 
use Equations 4.2.4–1 and 4.2.4–2 to evaluate Q˙
hk=1(Tj) and E ˙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 T
j, Q˙hk=1(Tj) <BL(T j) <Q˙hk=2(Tj). 
Calculate 
and d(T j) is evaluated using Equation 4.2.3– 
3 while, 
Q˙hk=i(Tj) = BL(T j), the space heating capacity 
delivered by the unit in matching the building load at temperature (T
j), 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 T
j, 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 . T j+ C . T j2. 
For each heat pump, determine the 
coefficients A, B, and C by conducting the 
following calculations once: 
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 (Q ˙
hk=1(T3) = BL(T 3)), °F. Determine T 3by equating Equations 
4.2.4–1 and 4.2–2 and solving for: 
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 H2
VTest, 
provides a space heating capacity that is equal to the building load (Q ˙hk=v(Tvh) = 
BL(T vh)), °F. Determine T vhby equating 
Equations 4.2.4–3 and 4.2–2 and solving for outdoor temperature. 
T
4= 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 (Q ˙
hk=2(T4) = BL(T 4)), °F. 
Determine T 4by equating Equations 
4.2.2–3 (k=2) and 4.2–2 and solving for outdoor temperature. 
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For multiple-split heat pumps (only), the 
following procedures supersede the above requirements for calculating COP hk=i(Tj). For 
each temperature bin where T 3> T j> T vh, 
4.2.4.3 Heat pump must operate 
continuously at maximum (k=2) compressor speed at temperature T j, BL(T j) ≥ Q˙hk=2(Tj). 
Evaluate the Equation 4.2–1 quantities 
as specified in section 4.2.3.4 with the 
understanding that Q ˙hk=2(Tj) and E ˙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, T
j, 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/lbm
da· °F) from the results 
of the H1 Test using: 
where VÔ
s,VÔ
mx,v′n(or v n), and W nare 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, 
Evaluate e h(Tj/N), RH(T j)/N, X(T j), PLF j, 
and d(T j) 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 T
o(Tj) is equal to or greater than T CC (the maximum supply temperature 
determined according to section 3.1.9), 
determine Q ˙h(Tj) and E ˙h(Tj) as specified in 
section 4.2.1 (i.e., Q˙h(Tj) = Q˙hp(Tj) and E ˙hp(Tj) 
= E˙hp(Tj)). Note: Even though T o(Tj) ≥ Tcc, 
resistive heating may be required; evaluate Equation 4.2.1–2 for all bins. Case 2. For outdoor bin temperatures 
where T
o(Tj) >T cc, determine Q ˙h(Tj) and E ˙h(Tj) 
using, 
Q˙h(Tj) = Q˙hp(Tj) + Q˙CC(Tj) 
E˙h(Tj) = E˙hp(Tj) + E˙CC(Tj) 
Where, 
Note: Even though T o(Tj) < T 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, T
j, 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 
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(expressed in Btu/lbm da· °F) from the results 
of the H1 2Test using: 
Where VÔ
s,VÔ
mx, v′ n(or v n), and W nare 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, 
Evaluate e h(Tj)/N, RH(T j)/N, X(T j), PLF j, 
and d(T j) as specified in section 4.2.1 with 
the exception of replacing references to the 
H1C Test and section 3.6.1 with the H1C 1 
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 T
o(Tj) is equal to or greater than T CC 
(the maximum supply temperature 
determined according to section 3.1.9), determine Q ˙
h(Tj) and E ˙h(Tj) as specified in 
section 4.2.2 (i.e. Q˙h(Tj) = Q˙hp(Tj) and E ˙h(Tj) 
= E˙hp(Tj)). Note: Even though T o(Tj) ≥ TCC, resistive heating may be required; evaluate 
Equation 4.2.1–2 for all bins. 
Case 2. For outdoor bin temperatures 
where T o(Tj) < T CC, determine Q ˙h(Tj) and 
E˙h(Tj) using, 
Q˙h(Tj) = Q˙hp(Tj) + Q˙CC(Tj)E ˙h(Tj) = E˙hp(Tj) 
+ E˙CC(Tj) 
Where, 
Note: Even though T o(Tj) < T 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, T
j, 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/lbm
da· °F) from the results of the H1 1 
Test using: 
Cp,da= 0.24 + 0.444 * W n 
Where 
VÔ
s,VÔ
mx, v′ n(or v n), and W nare 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, 
Repeat the above calculations to determine 
the mass flow rate (m ˙dak=2) and the specific 
heat of the indoor air (C p,dak=2) when operating at high capacity by using the 
results of the H1 2Test. 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, 
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Evaluate e h(Tj)/N, RH(T j)/N, Xk=1(Tj), and/ 
or Xk=2(Tj), PLF j, and d′(T j) or d″(T j) 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 T
ok=1(Tj) is equal to or greater than T CC 
(the maximum supply temperature determined according to section 3.1.9), determine Q ˙
hk=1(Tj) and E ˙hk=1(Tj) as specified in section 4.2.3 (i.e., Q˙hk=1(Tj) = Q˙hpk=1(Tj) and 
E˙hk=1(Tj) = E˙hpk=1(Tj). 
Note: Even though T ok=1(Tj) ≥ TCC, resistive 
heating may be required; evaluate RH(T j)/N 
for all bins. 
Case 2. For outdoor bin temperatures 
where T ok=1(Tj) < T CC, determine Q ˙hk=1(Tj) 
and E ˙hk=1(Tj) using, 
Note: Even though T ok=1(Tj) ≥Tcc, 
additional resistive heating may be required; 
evaluate RH(T j)/N for all bins. 
Case 3. For outdoor bin temperatures 
where T ok=2(Tj) is equal to or greater than 
TCC, determine Q ˙hk=2(Tj) and E ˙hk=2(Tj) as specified in section 4.2.3 (i.e., Q˙hk=2(Tj) = 
Q˙hpk=2(Tj) and E ˙hk=2(Tj) = E˙hpk=2(Tj)). 
Note: Even though T ok=2(Tj) < T CC, resistive 
heating may be required; evaluate RH(T j)/N 
for all bins. Case 4. For outdoor bin temperatures 
where T ok=2(Tj) < T CC, determine Q ˙hk=2(Tj) 
and E ˙hk=2(Tj) using, 
Note: Even though T ok=2(Tj) < T cc, 
additional resistive heating may be required; evaluate RH(T
j)/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 
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 °F ≤ T ≤ 65°F; At the high 
(k=2) compressor capacity, the outdoor temperature range of operation is 20 °F ≤ T 
≤ 50°F; At the booster (k=3) compressor 
capacity, the outdoor temperature range of 
operation is ¥20 °F ≤ T ≤ 30°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 Q˙
hk=1(Tj) and E ˙hk=1(Tj)) In evaluating the 
section 4.2.3 equations, Determine Q ˙hk=1(62) 
and E ˙hk=1(62) from the H0 1Test, Q ˙hk=1(47) 
and E ˙hk=1(47) from the H1 1Test, and 
Q˙hk=2(47) and E ˙hk=2(47) from the H1 2Test. Calculate all four quantities as specified in section 3.7. If, in accordance with section 3.6.6, the H3
1Test is conducted, calculate 
Q˙hk=1(17) and E ˙hk=1(17) as specified in section 
3.10 and determine Q ˙hk=1(35) and E ˙hk=1(35) as 
specified in section 3.6.6. 
b. Evaluate the space heating capacity and 
electrical power consumption (Q ˙hk=2(Tj) and 
E˙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 Q˙
hk=1(62) and E ˙hk=1(62) from the H0 1Test, 
Q˙hk=1(47) and E ˙hk=1(47) from the H1 1Test, 
and Q ˙hk=2(47) and E ˙hk=2(47) from the H1 2 
Test, evaluated as specified in section 3.7. Determine the equation input for Q ˙
hk=2(35) 
and E ˙hk=2(35) from the H2 2,evaluated as 
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specified in section 3.9.1. Also, determine 
Q˙hk=2(17) and E ˙hk=2(17) from the H3 2Test, 
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 
Determine Q ˙hk=3(17) and E ˙hk=3(17) from the 
H3 3Test and determine Q ˙hk=2(2) and E ˙hk=3(2) 
from the H4 3Test. Calculate all four 
quantities as specified in section 3.10. Determine the equation input for Q ˙hk=3(35) 
and E ˙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 T j, 
Q˙hk=1(Tj) ≥BL(T j)., and the heat pump permits 
low compressor capacity at T j.Evaluate the 
quantities 
using Eqs. 4.2.3–1 and 4.2.3–2, respectively. 
Determine the equation inputs Xk=1(Tj), PLF j, 
and d′(T j) as specified in section 4.2.3.1. In 
calculating the part load factor, PLF j, use the 
low-capacity cyclic-degradation coefficient CDh, [or equivalently, C Dh(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 T j and its capacity is greater than or equal to the 
building heating load, BL(T j) < Q˙hk=2(Tj). 
Evaluate the quantities 
as specified in section 4.2.3.3. Determine the 
equation inputs Xk=2(Tj), PLF j, and d′(T j) as 
specified in section 4.2.3.3. In calculating the 
part load factor, PLF j, use the high-capacity cyclic-degradation coefficient, C Dh(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 T j and its capacity is greater than or equal to the 
building heating load, BL(T j) ≤ Q˙hk=3(Tj). 
Determine the low temperature cut-out 
factor, d′(T j), using Eq. 4.2.3–3. Use the 
booster-capacity cyclic-degradation coefficient, C Dh(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 T
j, Q˙hk=1(Tj) < BL(T j) < 
Q˙hk=2(Tj). Evaluate the quantities 
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as specified in section 4.2.3.2. Determine the 
equation inputs Xk=1(Tj), Xk=2(Tj), and d′(T j) 
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 T
j, Q˙hk=2(Tj) <BL(T j) 
<Q˙hk=3(Tj). 
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, d′(T j), using Eq. 
4.2.3–3. 
4.2.6.6 Heat pump only operates at low 
(k=1) capacity at temperature T jand its capacity is less than the building heating load, BL(T
j) > Q˙hk=1(Tj). 
Where the low temperature cut-out factor, 
d′(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) > Q ˙hk=2(Tj).Evaluate the 
quantities 
as specified in section 4.2.3.4. Calculate 
d″(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(T
j) > Q˙hk=3(Tj). or the system 
converts to using only resistive heating. 
Where d″(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 T
j, set d′(T j) 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 e
h(Tj)/N and 
RH(T j)/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, 
Q˙hk=1(Tj), and electrical power consumption, 
E˙hk=1(Tj), of the heat pump when operating 
at the heating minimum air volume rate and outdoor temperature T
jusing Eqs. 4.2.2–3 
and 4.2.2–4, respectively. Use these same equations to calculate the space heating 
capacity, Q ˙hk=2(Tj) and electrical power 
consumption, E ˙hk=2(Tj), of the test unit when 
operating at the heating full-load air volume rate and outdoor temperature T
j. In 
evaluating Eqs. 4.2.2–3 and 4.2.2– 4, determine the quantities Q ˙
hk=1(47) and E ˙hk= 
1(47) from the H1 1Test; determine Q ˙hk=2(47) 
and E ˙hk=2(47) from the H1 2Test. Evaluate 
all four quantities according to section 3.7. Determine the quantities Q ˙
hk=1(35) and E ˙hk= 
1(35) as specified in section 3.6.2. Determine 
Q˙hk=2(35) and E ˙hk=2(35) from the H2 2Frost 
Accumulation Test as calculated according to section 3.9.1. Determine the quantities Q ˙
hk=1 
(17) and E ˙hk=1(17) from the H3 1Test, and 
Q˙hk=2(17) and E ˙hk=2(17) from the H3 2Test. 
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, CD
h, as per sections 3.6.2 and 3.8 to 3.8.1. Assign this same value 
to CD h(k = 2). 
c. Except for using the above values of Q ˙hk= 
1(Tj), E ˙hk=1(Tj), Q ˙hk=2(Tj), E ˙hk=2(Tj), CD h, 
and CD h(k = 2), calculate the quantities 
eh(Tj)/N as specified in section 4.2.3.1 for 
cases where Q ˙hk=1(Tj) ≥ BL(T j). For all other 
outdoor bin temperatures, T j, calculate e h(Tj)/ 
N and RH h(Tj)/N as specified in section 
4.2.3.3 if Q ˙hk=2(Tj) > BL(Tj) or as specified 
in section 4.2.3.4 if Q ˙hk=2(Tj) ≤ BL(T j) 
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 e
h(Tj)/N and 
RH(T j)/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: 
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less than 36,000 Btu/h, determine the off 
mode rating, P W,OFF , with the following 
equation: 
greater than or equal to 36,000 Btu/h, 
calculate the capacity scaling factor 
according to: 
Where, Q ˙C(95) is the total cooling capacity at 
the A or A 2Test condition, and 
determine 
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 · SSH; and the off mode 
energy consumption of a CAC, only, for the heating season, E2, using: E2 = P2 · 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 °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 °F to ¥23 °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—R EPRESENTATIVE COOLING AND HEATING LOADHOURS AND THE CORRESPONDING SET OF SEASONAL HOURS  
FOREACHGENERALIZED CLIMATIC REGION  
Climatic region Cooling load 
hours 
CLH R Heating load 
hours 
HLH R Cooling sea-
son hours 
CSH R Heating sea-
son hours 
HSH R Shoulder sea-
son hours 
SSH R 
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 
Region I: HSH = 2.4348HLH; Region II: HSH = 2.5182HLH; Region III: HSH = 2.5444HLH; 
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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 · CLH TABLE 22—F RACTIONAL BINHOURS  
FOR THE SHOULDER SEASON HOURS  
FORALLREGIONS  
Tj(°F) Fractional bin hours 
Air conditioners Heat pumps 
72 .......... 0.333 0.167 
67 .......... 0.667 0.333 TABLE 22—F RACTIONAL BINHOURS  
FOR THE SHOULDER SEASON HOURS  
FORALLREGIONS —Continued 
Tj(°F) Fractional bin hours 
Air conditioners Heat pumps 
62 .......... 0 0.333 
57 .......... 0 0.167 
4.3.4 For air conditioners, the annual off 
mode energy consumption, E TOTAL , is: E TOTAL  
= E1 + E2. 
4.3.5 For heat pumps, the annual off 
mode energy consumption, E TOTAL , 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 (APF A) for a particular location and for each standardized 
design heating requirement. 
Where, 
CLH A= the actual cooling hours for a 
particular location as determined using 
the map given in Figure 2, hr. 
Q˙ck(95) = the space cooling capacity of the 
unit as determined from the A or A 2 
Test, whichever applies, Btu/h. 
HLH A= 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·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·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 (APF
R) 
for each generalized climatic region and for each standardized design heating requirement. 
Where, 
CLH R= the representative cooling hours for 
each generalized climatic region, Table 
23, hr. 
HLH R= 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, Q ˙
ck(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—R EPRESENTATIVE COOLING  
AND HEATING LOAD HOURS FOR  
EACH GENERALIZED CLIMATIC RE-
GION 
Region CLH R HLH R 
I ................. 2400 750 
II ................ 1800 1250 
III ............... 1200 1750 
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TABLE 23—R EPRESENTATIVE COOLING  
AND HEATING LOAD HOURS FOR  
EACH GENERALIZED CLIMATIC RE-
GION—Continued 
Region CLH R HLH R 
IV .............. 800 2250 
V ............... 400 2750 TABLE 23—R EPRESENTATIVE COOLING  
AND HEATING LOAD HOURS FOR  
EACH GENERALIZED CLIMATIC RE-
GION—Continued 
Region CLH R HLH R 
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. 
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Figure 2-Cooling Load Hours (CLHA) for the United States 69397 Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules 
4.6 Calculations of the SHR, which 
should be computed for different equipment configurations and test conditions specified 
in Table 24. 
TABLE 24—A PPLICABLE TESTCONDITIONS FOR CALCULATION OF THE SENSIBLE HEATRATIO 
Equipment configuration Reference 
Table No. of 
Appendix M SHR computation with 
results from Computed values 
Units Having a Single-Speed Compressor and a Fixed-Speed Indoor 
blower, a Constant Air Volume Rate Indoor blower, or No Indoor blow-er.4 B Test ............................. SHR(B). 
Units Having a Single-Speed Compressor That Meet the Section 3.2.2.1 
Indoor Unit Requirements.5 B2 and B1 Tests ............ SHR(B1), SHR(B2). 
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: 
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, 
Where Q ˙ck(T) and E ˙ck(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., EER
A2) to 
differentiate among the resulting EER values. 
■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 P
W,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 § 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. 
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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 (C
D) means a 
parameter used in calculating the part load factor. The degradation coefficient for cooling is denoted by C
Dc. The degradation 
coefficient for heating is denoted by C Dh. 
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 
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, 
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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 °F 
increments that are used to partition the outdoor dry-bulb temperature ranges of the cooling (≥65 °F) and heating (<65 °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 °F outdoor 
dry bulb temperature and 80 °F dry bulb, 
67°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- 
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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 § 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 § 430.23 (m). For 
determination of certified rating requirements refer to § 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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Table 1 Informative Guidance for Using A 1 
Testing conditions Testing procedures Calculations 
Gen- Cool- Heat-
General General Cooling' Heating " era! ing . ing " 
2.1; 2.2a-c; 22.1; 2.2.4; 2.2.4.1; 
2.2.4.1 (1); 2.2.4.2; 2.2.5.1-5; 3.1; 3.1.1-3; 4.4; 
3.1.4.7; 3.1.10; 3.7a,h,d; 
Requirements for All units (except VRF) 22.5.7-g; 2.3; 2.3.1; 2.3.2; 2.4; 3.1.5-9; 3.11; I 3 3; 3.4; 3.5a-i 4.5; I 4.1 142 
3.8a,d; 3.8.1; 3.9; 3.10 
2.4.la,d; 2.5a-c; 2.5.1; 2.5.2- I 3.12 4.6 
2.5.4.2; 2.5.5-2.13 
3.1.4.4.1; 3.1.4.4.2; 
3.1.4.1.1; 3.1.4.l.la,b; 
Singk splil-sysl<.:m- blower coil 22a(l) 3.1.4.4.3a-b; 3.1.4.5.1; 
3. 1.4.2a-h; 3. 1.4.3a-h 
3.1.4.5.2a-c; 3.1.4.6a-b 
3.1.4.4.1; 3.1.4.42; 
3.1.4.4.k 
3.1.4.1.1; 3.1.4.1.1c; 
~ ,.Q c. c. " Singk splil-sysl<.:m- coil-only 22a( I); 2.2d,c;2.4d; 2.42 
3. 1.42c; 35. I 
3.1.4.5.2d; 
'· " Ei 
" = ::> 3.7c: 3.8b; 3.9f; 3.9.lb 
= " -5 Tri-split 2.2a(2) 
" .... 
::> 
~ g 
" c Ei 
!:: :§ 
·s " .... 
0" = " OJ] 
~ ..:: 
-; § 
= u Outdoor tmit with no match 2.2e 
Single-package 2.2.4.1(2); 2.2 5 6b; 2.4.1; 2.4.2 3.1.4.1 1:3.1.4.1 la,h; 
3.1.42a-b; 3.1.4.3a-b 3.1.4.4.1; 3.1.4.4.2; 
3.1.4.4 3a-b; 3.1.4.51; 
3.1.4.5.2a-c; 3.1.4.Ga-b 
3 Ei 
"0 ~ 
"0 £. < Heat pump 2.2.5.6.a 69402 Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules 
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Heating-only heat pump 3.1.7 3.1.4.1.1 Table 4 3.1.4.4.3 
3.1.4.4.2c; 
Two-capacily norlhem heal pLUnp 3.2.3c 3.6.3 
3. 1.4.5.2 c-d 
Triple-capacity northem heat pLUnp 3.2.5 3.6.6 4.2.6 
SDHV (non-VRF) 2.2b; 2.4.lc; 2.5.4.3 
3.1.4.4. I; 3.1.4.4.2; 
Single-.wne-mulli-coil splil and non- 3.1.4.1.1; 3.1.4.1.1a-b; 
2.2a( I ).(3); 2.2.3; 2.4.1 b 3.1.4.4 3a-b; 3.1.4.51; 
VRF multiple-split with duct 3.1.4.2a-b; 3.1.4.3a-b 
3.1.4.5.2a-c; 3.1.4.6a-h 
3.1.4.1.2; 3.1.4.2d; 
Single-zone-multi-coil split and non- 3.1.4.4.4; 3.1.4.5.2e; 3.1.4.6c; 
2.2.a(l ),(3 ); 2.2.3 31.43c; 3.2.4c; 
VRF multiple-split, ductless 3.6.4.c; 3.8c 
3.5c,g,h; 3.5.2; 3.8c 
2.1; 2.2.a; 2.2 h; 2.2.c; 2.2.1; 2.2 2; 3.1 (except 3.3-3.5 3.7-3.10 4.4; 
VRF multiple-splitt m1d 
2.2.3(a); 2.2.3(c);, 2.2.4; 2.2.5; 2.4- 3.1.3, 3.1.4) 4.5; 
4.1 4.2 
VRFSDHVt 2.12 3.1.4.1.k 4.6 
3.11-3.13 
Single speed compressor, fLxed speed fan 3.2.1 3.6.1 4.1.1 4.2.1 
Single speed compressor, VA V fan 3.1.7 3.2.2 3.6.2 4.1.2 4.2.2 
I .eo Two-capacity compressor 3.1.10 3.2.3 3.6.3 4.1.3 4.2.3 = :c .. Variable speed compressor 3.2.4 3.6.4 4.1.4 4.2.4 =-.. u 
Heat pump with heat comfmt controller 3.1.9 3.6.5 4.2.5 
~ 
~ Units with a multi-speed outdoor fan 2.2.2 
-= " Single indoor unil having mLtlliple "' r;.. 
:;; 3.26 3.6.2; 3.6.7 4.1.5 4.2.7 
·;::; blowers "' =-(/). 69403 Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules 
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 
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*Does not apply to heating-only heat pumps. 
**Applies only to heat pumps; not to air conditioners. 
tuse 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 
section4.7 to determine the energy efficiency ratio. 69404 Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules 
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 § 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 § 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 § 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 § 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 § 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·ft
2· °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 × L
f× Wf× Nf÷ Q˙c(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. 
Q˙c(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- 
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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 § 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 °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 °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 § 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 A
2test. 
(2) For cooling and heating heat pumps 
that do not function in the H1 or H1 2test 
with the charge set for the A or A 2test and 
for heating-only heat pumps, use the H1 or H1
2test. 
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 °F for fixed orifice systems or set subcooling to a target value of 10 °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 °F 
2. Subcooling: ±0.6 °F 
3. High side pressure or corresponding 
saturation or dew point temperature: 
±4.0 psi or ±1.0 °F 
4. Low side pressure or corresponding 
saturation or dew point temperature: ±2.0 psi or ±0.8 °F 
5. High side temperature: ±2.0 °F 
6. Low side temperature: ±2.0 °F 
7. Approach temperature: ±1.0 °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 
A
2test, the conditions are not within the 
range specified in manufacturer’s instructions for the H1 or H1
2test, make as 
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small as possible an adjustment to obtain 
conditions for this test in the specified range. After this adjustment, recheck conditions in the A or A
2test 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·ft
2· °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 § 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—S IZE OF OUTLET PLENUM  
Cooling full-load air volume 
rate 
(scfm) Maximum di-
ameter * 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, cal-
culate 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 § 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 § 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 
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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 °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 · ft
2 
·°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·ft
2·°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 § 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·ft
2· °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 § 430.3) and 
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section 5.2.2 of ASHRAE Standard 41.2–87 
(RA 92) (incorporated by reference, see § 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 § 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 § 430.3). The temperature sensor (wick removed) must be accurate to within ±0.2 °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 °F when operated 
at conditions that result in the evaluation of dew points above 35 °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 § 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 § 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 
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alternative approach when testing a unit 
charged with a zeotropic refrigerant having a temperature glide in excess of 1 °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 °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 § 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 § 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 § 430.3). The maximum and minimum temperatures measured by these sensors may differ by no more than 1.5 °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 · ft
2 
·°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, A
2, A1, B, B 2, B1, C, 
C1, EV, F 1, G1, H0 1, H1, H1 2, H1 1, HI N, H3, H3 2, and H3 1Tests), 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 § 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 H
2O 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 A
2 
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; 
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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 Q
Var, defined as follows, greater than 10 
percent. 
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 A
2 
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—M INIMUM EXTERNAL STATIC PRESSURE FOR DUCTED SYSTEMS TESTED WITH AN INDOOR BLOWER INSTALLED  
Rated Cooling1or heating2capacity 
(Btu/h) Minimum external static pressure3 
(Inches of water) 
Short ducted 
systems6 Small-duct, 
high-velocity 
systems45 All other 
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 
1For 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 A2Test conditions. 
2For 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. 
3For 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. 
4See section 1.2, Definitions, to determine if the equipment qualifies as a small-duct, high-velocity system. 
5If 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. 
6See 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, DP
st_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. 
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Where: 
DPst_i= target minimum external static 
pressure for test i; 
DPst_full= minimum external static pressure 
for test A or A 2(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 A
1, B1, C1, F1, and G 1Tests)— 
at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation Q
Var, 
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 E
VTest at an external static pressure that 
does not cause an automatic shutdown of the indoor blower or air volume rate variation Q
Var, 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 E
VTest 
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 A
2) and the H1 (or H1 2) Tests; 
2. Ducted heat pumps tested with constant- 
air-flow indoor blowers installed that provide the same air flow for the A (or A
2) and the 
H1 (or H1 2) 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 Q
Var, 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 A
2) 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 Q
Var, 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. 
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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 H1
2 
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 Q
Var, 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 H1
2Test, (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 A
1and the H1 1tests; 2. Ducted heat pumps 
tested with constant-air-flow indoor blowers installed that provide the same air flow for the A
1and the H1 1Tests; 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 Q
Var, 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 A
1cooling 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 H0
1, 
H1 1, H2 1, and H3 1Tests)—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 Q
Var, 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 
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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 H2
VTest at an external static 
pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation Q
Var, 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 H2
VTest 
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 °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 °F of the required inlet conditions. 
3.1.6 Air volume rate calculations. For all steady-state tests and for Frost 
Accumulation (H2, H2
1, H2 2, H2 V) 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: 
where, 
VÔ
s= air volume rate of standard (dry) air, (ft3/ 
min) da 
VÔ
mx= air volume rate of the air-water vapor 
mixture, (ft3/min) mx vn′ = specific volume of air-water vapor 
mixture at the nozzle, ft3per 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/ft3) 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
3per lbm of dry air. 
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 A
2Test 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 H1
2Test 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 E
VTest, and the first test using the Heating Minimum Air Volume Rate must 
precede the H2 VTest. 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 °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 °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 H1
2 
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, T
CC. 
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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, C
Dc. If testing outdoor units of central air conditioners or 
heat pumps that are not sold with indoor units, assign C
Dcthe default value of 0.2. 
Table 4 specifies test conditions for these four tests. 
TABLE 4—C OOLING MODETESTCONDITIONS FOR UNITS HAVING A SINGLE -SPEED COMPRESSOR AND A FIXED-SPEED  
INDOOR BLOWER , ACONSTANT AIRVOLUME RATEINDOOR BLOWER , ORNOINDOOR BLOWER  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Cooling air volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
A Test—required (steady, wet coil) .. 80 67 95 175 Cooling full-load.2 
B Test—required (steady, wet coil) .. 80 67 82 165 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). 
1The specified test condition only applies if the unit rejects condensate to the outdoor coil. 
2Defined in section 3.1.4.1. 
3The 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 °F or less be used.) 
4Maintain 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 A
2, A1, B2, and B 1Tests. Use the two dry- 
coil tests, the steady-state C 1Test and the 
cyclic D 1Test, to determine the cooling mode 
cyclic degradation coefficient, C/_128. 
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—C OOLING MODETESTCONDITIONS FOR UNITS WITH A SINGLE -SPEED COMPRESSOR THATMEET THE SECTION  
3.2.2.1 I NDOOR UNITREQUIREMENTS  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Cooling air volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
A2Test—required (steady, wet coil) ........ 80 67 95 175 Cooling full-load.2 
A1Test—required (steady, wet coil) ........ 80 67 95 175 Cooling minimum.3 
B2Test—required (steady, wet coil) ........ 80 67 82 165 Cooling full-load.2 
B1Test—required (steady, wet coil) ........ 80 67 82 165 Cooling minimum.3 
C1Test4—required (steady, dry coil) ....... 80 (4) 82 ........................ Cooling minimum.3 
D1Test4—required (cyclic, dry coil) ......... 80 (4) 82 (5) 
1The specified test condition only applies if the unit rejects condensate to the outdoor coil. 
2Defined in section 3.1.4.1. 
3Defined in section 3.1.4.2. 
4The 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 °F or less be used.) 
5Maintain 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 1Test. 
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 A 2, B2, B1, and F 1Tests. Use the two dry- 
coil tests, the steady-state C 1Test and the 
cyclic D 1Test, to determine the cooling-mode 
cyclic-degradation coefficient, C/_128. 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 B
1 
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 C
2Test 
and the cyclic D 2Test, to determine the 
cooling-mode cyclic-degradation coefficient that only applies to on/off cycling from high capacity, C/_128(k=2). The default C
Oc(k=2) is the 
same value as determined or assigned for the low-capacity cyclic-degradation coefficient, C/_128 [or equivalently, C/_128(k=1)]. 
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TABLE 6—C OOLING MODETESTCONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor 
capacity Cooling air volume 
rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
A2Test—required (steady, wet coil) ....... 80 67 95 175 High ....................... Cooling Full-Load.2 
B2Test—required (steady, wet coil) ....... 80 67 82 165 High ....................... Cooling Full-Load.2 
B1Test—required (steady, wet coil) ....... 80 67 82 165 Low ........................ Cooling Minimum.3 
C2Test—required (steady, dry-coil) ....... 80 (4) 82 High Cooling Full-Load.2 
D2Test—required (cyclic, dry-coil) ......... 80 (4) 82 High (5) ...........................
C1Test—required (steady, dry-coil) ....... 80 (4) 82 Low Cooling Minimum.3 
D1Test—required (cyclic, dry-coil) ......... 80 (4) 82 Low (6) ...........................
F1Test—required (steady, wet coil) ....... 80 67 67 153.5 Low ........................ Cooling Minimum.3 
1The specified test condition only applies if the unit rejects condensate to the outdoor coil. 
2Defined in section 3.1.4.1. 
3Defined in section 3.1.4.2. 
4The 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 °F or less. 
5Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the C 2Test. 
6Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the C 1Test. 
3.2.4 Tests for a unit having a variable- 
speed compressor. 
a. Conduct five steady-state wet coil tests: 
The A 2, EV, B2, B1, and F 1Tests. Use the two dry-coil tests, the steady-state G 1Test and the 
cyclic I 1Test, to determine the cooling mode 
cyclic degradation coefficient, C Dc..-Table-7 
specifies test conditions for these seven tests. Determine the intermediate compressor 
speed cited in Table 7 using: 
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 F
1Test. 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 E
V 
Test, a cooling-mode intermediate compressor speed that falls within 
1⁄4and 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 E
VTest 
conditions and bracketed compressor speed range. The manufacturer can designate that one or more indoor units are turned off for the E
VTest. 
TABLE 7—C OOLING MODETESTCONDITION FOR UNITS HAVING A VARIABLE -SPEED COMPRESSOR  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor speed Cooling air volume 
rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
A2Test—required (steady, wet coil) ....... 80 67 95 175 Maximum ............... Cooling Full-Load.2 
B2Test—required (steady, wet coil) ....... 80 67 82 165 Maximum ............... Cooling Full-Load.2 
EVTest—required (steady, wet coil) ....... 80 67 87 169 Intermediate ........... Cooling Inter-
mediate.3 
B1Test—required (steady, wet coil) ....... 80 67 82 165 Minimum ................ Cooling Minimum.4 
F1Test—required (steady, wet coil) ....... 80 67 67 153.5 Minimum ................ Cooling Minimum.4 
G1Test5—required (steady, dry-coil) ..... 80 (6) 67 Minimum Cooling Minimum.4.
I1Test5—required (cyclic, dry-coil) ......... 80 (6) 67 Minimum (6).
1The specified test condition only applies if the unit rejects condensate to the outdoor coil. 
2Defined in section 3.1.4.1. 
3Defined in section 3.1.4.3. 
4Defined in section 3.1.4.2. 
5The 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 °F or less. 
6Maintain 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 G 1Test. 
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. 
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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, A
2, A1, B, B 2, 
B1, EV, and F 1Tests). 
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 § 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 Q ˙ck(T), 
Q˙sck(T) and E ˙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 Q ˙
ck(T) by 
where VÔ
sis the average measured indoor air 
volume rate expressed in units of cubic feet 
per minute of standard air (scfm). 
TABLE 8—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR SECTION 3.3 S TEADY -STATE WETCOILCOOLING  
MODETESTS AND SECTION 3.4 D RYCOILCOOLING MODETESTS  
Test operating 
tolerance1 Test condition 
tolerance1 
Indoor dry-bulb, °F: 
Entering temperature ........................................................................................................... ............................. 2.0 0.5 
Leaving temperature ......................................................................................................................................... 2.0 
Indoor wet-bulb, °F: 
Entering temperature ........................................................................................................... ............................. 1.0 20.3 
Leaving temperature .........................................................................................................................................21.0 
Outdoor dry-bulb, °F: 
Entering temperature ........................................................................................................... ............................. 2.0 0.5 
Leaving temperature .........................................................................................................................................32.0 
Outdoor wet-bulb, °F: 
Entering temperature ........................................................................................................... ............................. 1.0 40.3 
Leaving temperature .........................................................................................................................................31.0 
External resistance to airflow, inches of water ................................................................................ ........................ 0.12 50.02 
Electrical voltage, % of rdg. .................................................................................................. ................................... 2.0 1.5 
Nozzle pressure drop, % of rdg. ............................................................................................................................. 8.0 
1See section 1.2, Definitions. 
2Only applies during wet coil tests; does not apply during steady-state, dry coil cooling mode tests. 
3Only applies when using the Outdoor Air Enthalpy Method. 
4Only applies during wet coil cooling mode tests where the unit rejects condensate to the outdoor coil. 
5Only 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 (DP
min) by 0.03 inches 
of water or more. 1. Measure the average power consumption 
of the indoor blower motor (E ˙fan,1) and record 
the corresponding external static pressure (DP
1) during or immediately following the 30- 
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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 DP
1+ (DP 1¥ DPmin). 
3. After re-establishing steady readings of 
the fan motor power and external static pressure, determine average values for the 
indoor blower power (E ˙
fan,2) and the external static pressure (DP 2) by making 
measurements over a 5-minute interval. 
4. Approximate the average power 
consumption of the indoor blower motor at 
DPminusing linear extrapolation: 
5. Increase the total space cooling capacity, 
Q˙ck(T), by the quantity (E ˙fan,1¥ E˙fan,min ), 
when expressed on a Btu/h basis. Decrease 
the total electrical power, E ˙ck(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, C 1, C2, and 
G1Tests). 
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 Q ˙
ss,dry and E ˙ss,dry. With regard to a section 3.3 deviation, do not adjust Q ˙ss,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, VÔ, 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, W n, 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, DT (Set SS) and DT (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: 
Each time a subsequent set of temperature 
differences is recorded (if sampling more 
frequently than every 5 minutes), calculate 
FCDusing the most recent seven sets of 
values. Continue these calculations until the 30-minute period is completed or until a value for F
CDis 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 F
CDare within the allowable range, 
save the final value of the ratio from the 30- minute test as F
CD*. 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 F
CD*= 1. 
3.5 Test procedures for the cyclic dry-coil 
cooling-mode tests (the D, D 1, D2, and I 1 
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 (Dt
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 (Dt
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 °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 
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(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 C
Dfor each complete 
active cycle if the test tolerances given in Table 9 are satisfied. If the average C
Dfor the 
first three active cycles is within 0.02 of the average C
Dfor the first two active cycles, use 
the average C Dof the three active cycles as the final result. If these averages differ by more than 0.02, continue the test to get C
D 
for the fourth cycle. If the average C Dof the 
last three cycles is lower than or no more than 0.02 greater than the average C
Dof the 
first three cycles, use the average C Dof all 
four active cycles as the final result. Otherwise, continue the test with a fifth cycle. If the average C
Dof the last three 
cycles is 0.02 higher than the average for the previous three cycles, use the default C
D, 
otherwise use the average C Dof all five active 
cycles. If the test tolerances given in Table 9 are not satisfied, use default C
Dvalue. The 
default C Dvalue 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 Dt
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—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR CYCLIC DRYCOILCOOLING MODETESTS  
Test 
operating 
tolerance1 Test 
condition 
tolerance1 
Indoor entering dry-bulb temperature,2°F .............................................................................................................. 2.0 0.5 
Indoor entering wet-bulb temperature, °F ............................................................................................................... ........................ (3) 
Outdoor entering dry-bulb temperature,2°F ............................................................................................................ 2.0 0.5 
External resistance to airflow,2inches of water ...................................................................................................... 0.12 ........................
Airflow nozzle pressure difference or velocity pressure,2% of reading ................................................................. 8.0 42.0 
Electrical voltage,5% of rdg ..................................................................................................................................... 2.0 1.5 
1See section 1.2, Definitions. 
2Applies 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. 
3Shall at no time exceed a wet-bulb temperature that results in condensate forming on the indoor coil. 
4The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state dry coil test. 
5Applies during the interval when at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are oper-
ating 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 e cyc,dry and 
express it in units of watt-hours. Calculate the total space cooling delivered, q cyc,dry , in 
units of Btu using, 
where VÔ, Cp,a, vn′ (or v n), W n, and F CD* are 
the values recorded during the section 3.4 
dry coil steady-state test and 
Tal(t) = dry bulb temperature of the air 
entering the indoor coil at time t, °F. 
Ta2(t) = dry bulb temperature of the air 
leaving the indoor coil at time t, °F. 
t1= 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. t
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 
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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 e
cyc,dry by the quantity, 
Equation 3.5–2 (441W÷1000scfm) * VÔ* 
[t2¥t 1] 
and decrease q cyc,dry by, 
Equation 3.5–3 (1505 Btu/h÷1000scfm) * VÔ 
* [t 2¥t 1] 
where VÔ
sis 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 e
cyc,dry and decrease q cyc,dry based on: 
a. The product of [t 2¥t 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 e
cyc,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, e
cyc,dry . Add the electrical 
energy used by the indoor blower during the 3 minutes after compressor cutoff to the integrated cooling capacity, q
cyc,dry . For the 
case where the non-ducted unit uses a variable-speed indoor blower which is disabled during the cyclic test, correct e
cyc,dry  
and q cyc,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, C
Dc. Append ‘‘(k=2)’’ to the coefficient if it 
corresponds to a two-capacity unit cycling at high capacity. Evaluate C
Dcusing the above 
results and those from the section 3.4 dry- coil steady-state test. 
the average energy efficiency ratio during the 
cyclic dry coil cooling mode test, Btu/W·h 
the average energy efficiency ratio during the steady-state dry coil cooling mode test, Btu/ 
W·h 
Round the calculated value for C Dcto the 
nearest 0.01. If C Dcis 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, C
Dh. Test 
conditions for the four tests are specified in Table 10. 
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TABLE 10—H EATING MODETESTCONDITIONS FOR UNITS HAVING A SINGLE -SPEED COMPRESSOR AND A FIXED-SPEED  
INDOOR BLOWER , ACONSTANT AIRVOLUME RATEINDOOR BLOWER , ORNOINDOOR BLOWER  
Test description Air entering indoor unit 
temperature 
(°F) Air entering outdoor unit 
temperature 
(°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 
1Defined in section 3.1.4.4. 
2Maintain 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 (H1
2and H1 1), one Frost Accumulation 
Test (H2 2), and two Low Temperature Tests 
(H3 2and H3 1). Conducting an additional 
Frost Accumulation Test (H2 1) is optional. 
Conduct the High Temperature Cyclic (H1C 1) 
Test to determine the heating mode cyclic- degradation coefficient, C Dh. Test conditions 
for the seven tests are specified in Table 11. If the optional H2
1Test is not performed, use 
the following equations to approximate the capacity and electrical power of the heat pump at the H2
1test conditions: 
The quantities Q ˙hk=2(47), E ˙hk=2(47), 
Q˙hk=1(47), and E ˙hk=1(47) are determined from 
the H1 2and H1 1Tests and evaluated as 
specified in section 3.7; the quantities Q˙hk=2(35) and E ˙hk=2(35) are determined from 
the H2 2Test and evaluated as specified in 
section 3.9; and the quantities Q ˙hk=2(17), 
E˙hk=2(17), Q ˙hk=1(17), and E ˙hk=1(17), are determined from the H3 2and H3 1Tests and 
evaluated as specified in section 3.10. 
TABLE 11—H EATING MODETESTCONDITIONS FOR UNITS WITH A SINGLE -SPEED COMPRESSOR THATMEET THE SECTION  
3.6.2 I NDOOR UNITREQUIREMENTS  
Test description Air entering indoor unit 
temperature 
(°F) Air entering outdoor unit 
temperature 
(°F) Heating air volume rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
H12Test (required, steady) ...................... 70 60(max) 47 43 Heating Full-load.1 
H11Test (required, steady) ...................... 70 60(max) 47 43 Heating Minimum.2 
H1C 1Test (required, cyclic) ...................... 70 60(max) 47 43 (3). 
H22Test (required) ................................... 70 60(max) 35 33 Heating Full-load.1 
H21Test (optional) .................................... 70 60(max) 35 33 Heating Minimum.2 
H32Test (required, steady) ...................... 70 60(max) 17 15 Heating Full-load.1 
H31Test (required, steady) ...................... 70 60(max) 17 15 Heating Minimum.2 
1Defined in section 3.1.4.4. 
2Defined in section 3.1.4.5. 
3Maintain 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 1Test. 
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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 (H0
1), two High Temperature Tests 
(H1 2and H1 1), one Frost Accumulation Test 
(H2 2), and one Low Temperature Test (H3 2). Conduct an additional Frost Accumulation 
Test (H2 1) and Low Temperature Test (H3 1) 
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 °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°F and less. 
If the above two conditions are met, an 
alternative to conducting the H2
1Frost 
Accumulation is to use the following equations to approximate the capacity and electrical power: 
Determine the quantities Q ˙hk=1(47) and 
E˙hk=1(47) from the H1 1Test and evaluate 
them according to Section 3.7. Determine the 
quantities Q ˙hk=1(17) and E ˙hk=1(17) from the 
H3 1Test and evaluate them according to 
Section 3.10. b. Conduct the High Temperature Cyclic 
Test (H1C 1) to determine the heating mode 
cyclic-degradation coefficient, C Dh. If a two- 
capacity heat pump locks out low capacity operation at lower outdoor temperatures, 
conduct the High Temperature Cyclic Test (H1C
2) to determine the high-capacity 
heating mode cyclic-degradation coefficient, 
CDh(k=2). Table 12 specifies test conditions 
for these nine tests. 
TABLE 12—H EATING MODETESTCONDITIONS FOR UNITS HAVING A TWO-CAPACITY COMPRESSOR  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor capac-
ity Heating air volume 
rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
H01Test (required, steady) .................... 70 60 (max) 62 56.5 Low ........................ Heating Minimum.1 
H12Test (required, steady) .................... 70 60(max) 47 43 High ....................... Heating Full-Load.2 
H1C 2Test (required,7cyclic) .................. 70 60(max) 47 43 High ....................... (3) 
H11Test (required) ................................. 70 60(max) 47 43 Low ........................ Heating Minimum.1 
H1C 1Test (required, cyclic) .................... 70 60(max) 47 43 Low ........................ (4) 
H22Test (required) ................................. 70 60(max) 35 33 High ....................... Heating Full-Load.2 
H21Test56(required) ............................. 70 60(max) 35 33 Low ........................ Heating Minimum.1 
H32Test (required, steady) .................... 70 60(max) 17 15 High ....................... Heating Full-Load.2 
H31Test5(required, steady) .................. 70 60(max) 17 15 Low ........................ Heating Minimum.1 
1Defined in section 3.1.4.5. 
2Defined in section 3.1.4.4. 
3Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H1 2Test. 
4Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H1 1Test. 
5Required only if the heat pump’s performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is need-
ed to complete the section 4.2.3 HSPF calculations. 
6If table note #5 applies, the section 3.6.3 equations for Q ˙hk=1(35) and E ˙hk=1(17) may be used in lieu of conducting the H2 1Test. 
7Required 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 (H0 1), two High Temperature Tests (H1 2 
and H1 1), one Frost Accumulation Test 
(H2 V), and one Low Temperature Test (H3 2). 
Conducting one or all of the following tests 
is optional: An additional High Temperature 
Test (H1 N), an additional Frost Accumulation 
Test (H2 2), and an additional Low 
Temperature Test (H4 2). Conduct the High Temperature Cyclic (H1C 1) Test to determine 
the heating mode cyclic-degradation 
coefficient, C Dh. (2) The optional low 
ambient temperature test (H4 2) may be 
conducted in place of H1 2to allow 
representation of heating performance below 17 °F ambient temperature using the results 
of H4
2and H3 2rather than the results of H3 2 
and H1 2. This option may not be used for 
units which have a cutoff temperature 
preventing compressor operation below 12 °F. If H4 2is conducted, it is optional to 
conduct the H1 2test for heating capacity 
rating purposes—H1 Ncan be conducted for 
heating capacity rating purposes. If H1 2is not 
conducted, H2 2must 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: 
Where a tolerance of plus 5 percent or the 
next higher inverter frequency step from that calculated is allowed. If the H2 2Test is not 
done, use the following equations to approximate the capacity and electrical power at the H2
2test conditions: 
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b. Determine the quantities Q ˙hk=2(47) and 
from E ˙hk=2(47) from the H1 2Test and 
evaluate them according to section 3.7. 
Determine the quantities Q ˙hk=2(17) and 
E˙hk=2(17) from the H3 2Test and evaluate 
them according to section 3.10. Determine the quantities Q ˙hk=2(TL) and E ˙hk=2(TL) from 
the H4 2Test 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 H1
NTest if the manufacturer requests it. If the H1 NTest 
is done, operate the heat pump’s compressor 
at the same speed as the speed used for the cooling mode A
2Test. 
TABLE 13—H EATING MODETESTCONDITIONS FOR UNITS HAVING A VARIABLE -SPEED COMPRESSOR  
Test description Air entering indoor unit 
temperature (°F) Air entering outdoor unit 
temperature (°F) Compressor speed Heating air volume 
rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
H01Test (required, steady) ..................... 70 60(max) 62 56.5 Minimum ................ Heating Minimum.1 
H1C 1Test (required, cyclic) .................... 70 60(max) 47 43 Minimum ................ (2). 
H12Test (required, steady) ..................... 70 60(max) 47 43 Maximum ............... Heating Full-Load.3 
H11Test (required, steady) ..................... 70 60(max) 47 43 Minimum ................ Heating Minimum.1 
H1NTest (optional, steady) ..................... 70 60(max) 47 43 Cooling Mode Max-
imum.Heating Nominal.4 
H22Test (optional) .................................. 70 60(max) 35 33 Maximum ............... Heating Full-Load.3 
H2VTest (required) ................................. 70 60(max) 35 33 Intermediate ........... Heating Inter-
mediate.5 
H32Test (required, steady) ..................... 70 60(max) 17 15 Maximum ............... Heating Full-Load.3 
H42Test (optional, steady)6................... 70 60(max) 72 71 Maximum8............. Heating Full-Load.3 
1Defined in section 3.1.4.5. 
2Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as meas-
ured during the H0 1Test. 
3Defined in section 3.1.4.4. 
4Defined in section 3.1.4.7. 
5Defined in section 3.1.4.6. 
6If the maximum speed is limited below 17 °F, this test becomes required. 
7If the cutoff temperature is higher than 2 °F, run at the cutoff temperature. 
8If 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 dif-
ferent 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 H2
V 
Test, a heating mode intermediate 
compressor speed that falls within 1⁄4and 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 H2
VTest 
conditions and bracketed compressor speed range. The manufacturer can designate that one or more specific indoor units are turned off for the H2
VTest. 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 
(H0
1), two high-temperature tests (H1 2and H1 1), one Frost Accumulation test (H2 2), two 
low-temperature tests (H3 2, H3 3), and one 
minimum-temperature test (H4 3). Conduct an 
additional Frost Accumulation test (H2 1) and 
low-temperature test (H3 1) 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 °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 °F and less. If the above two conditions are met, an alternative to conducting the H2
1Frost 
Accumulation Test to determine Q ˙hk=1(35) 
and E ˙hk=1(35) is to use the following 
equations to approximate this capacity and electrical power: 
In evaluating the above equations, determine 
the quantities Q ˙hk=1(47) from the H1 1Test and evaluate them according to section 3.7. Determine the quantities Q ˙
hk=1(17) and E˙hk=1(17) from the H3 1Test and evaluate 
them according to section 3.10. Use the 
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paired values of Q ˙hk=1(35) and E ˙hk=1(35) 
derived from conducting the H2 1Frost 
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 
(H2
3) with the heat pump operating at its 
booster capacity is optional. If this optional test is not conducted, determine Q ˙hk=3(35) 
and E ˙hk=3(35) using the following equations 
to approximate this capacity and electrical 
power: 
Determine the quantities Q ˙hk=2(47) and 
E˙hk=2(47) from the H1 2Test and evaluate 
them according to section 3.7. Determine the 
quantities Q ˙hk=2(35) and E ˙hk=2(35) from the 
H2 2Test and evaluate them according to 
section 3.9.1. Determine the quantities Q˙
hk=2(17) and E ˙hk=2(17) from the H3 2Test, 
determine the quantities Q ˙hk=3(17) and 
E˙hk=3(17) from the H3 3Test, and determine 
the quantities Q ˙hk=3(2) and E ˙hk=3(2) from the 
H4 3Test. Evaluate all six quantities according 
to section 3.10. Use the paired values of Q˙
hk=3(35) and E ˙hk=3(35) derived from 
conducting the H2 3Frost 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 
(H1C
1) to determine the heating mode cyclic- 
degradation coefficient, C Dh. If a triple- 
capacity heat pump locks out low capacity operation at lower outdoor temperatures, conduct the high-temperature cyclic test (H1C
2) to determine the high-capacity 
heating mode cyclic-degradation coefficient, C
Dh(k=2). The default C Dh(k=2) is the same value as determined or assigned for the low- capacity cyclic-degradation coefficient, C
Dh 
[or equivalently, C Dh(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 (H3C
3) to determine 
the booster-capacity heating mode cyclic- degradation coefficient, C
Dh(k=3). The 
default C Dh(k=3) is the same value as 
determined or assigned for the high-capacity cyclic-degradation coefficient, C
Dh[or 
equivalently, C Dh(k=2)]. Table 14 specifies 
test conditions for all 13 tests. 
TABLE 14— H EATING MODETESTCONDITIONS FOR UNITS WITH A TRIPLE -CAPACITY COMPRESSOR  
Test description Air entering indoor unit tem-
perature 
°F Air entering outdoor unit tem-
perature 
°F Compressor capacity Heating air volume 
rate 
Dry bulb Wet bulb Dry bulb Wet bulb 
H01Test (required, 
steady).70 60(max) 62 56 .5 Low ............................. Heating Minimum.1 
H12Test (required, 
steady).70 60(max) 47 43 High ............................ Heating Full-Load.2 
H1C 2Test (required, 
cyclic).70 60(max) 47 43 High ............................ (3) 
H11Test (required) ...... 70 60(max) 47 43 Low ............................. Heating Minimum.1 
H1C 1Test (required, 
cyclic).70 60(max) 47 43 Low ............................. (4) 
H23Test (optional, 
steady).70 60(max) 35 33 Booster ....................... Heating Full-Load.2 
H22Test (required) ...... 70 60(max) 35 33 High ............................ Heating Full-Load.2 
H21Test (required) ...... 70 60(max) 35 33 Low ............................. Heating Minimum.1 
H33Test (required, 
steady).70 60(max) 17 15 Booster ....................... Heating Full-Load.2 
H3C 3Test(max)5 6 (re-
quired, cyclic).70 60(max) 17 15 Booster ....................... (7) 
H32Test (required, 
steady).70 60(max) 17 15 High ............................ Heating Full-Load.2 
H31Test5(required, 
steady).70 60(max) 17 15 Low ............................. Heating Minimum.1 
H43Test (required, 
steady).70 60(max) 2 1 Booster ....................... Heating Full-Load.2 
1Defined in section 3.1.4.5. 
2Defined in section 3.1.4.4. 
3Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H1 2Test. 
4Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H1 1Test. 
5Required only if the heat pump’s performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is need-
ed to complete the section 4.2.6 HSPF calculations. 
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6If table note5applies, the section 3.6.6 equations for Q ˙hk=1(35) and E ˙hk=1(17) may be used in lieu of conducting the H2 1Test. 
7Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as meas-
ured during the H3 3Test. 
3.7 Test procedures for steady-state 
Maximum Temperature and High 
Temperature heating mode tests (the H0 1, H1, 
H1 2, H1 1, and H1 NTests). 
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—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR SECTION 3.7 ANDSECTION 3.10 S TEADY -STATE 
HEATING MODETESTS  
Test 
operating toler-
ance1 Test 
condition toler-
ance1 
Indoor dry-bulb, °F: 
Entering temperature ........................................................................................................... ......................... 2 .0 0 .5 
Leaving temperature ............................................................................................................ ......................... 2 .0 ..........................
Indoor wet-bulb, °F: 
Entering temperature ........................................................................................................... ......................... 1 .0 ..........................
Leaving temperature ............................................................................................................ ......................... 1 .0 ..........................
Outdoor dry-bulb, °F: 
Entering temperature ........................................................................................................... ......................... 2 .0 0 .5 
Leaving temperature ............................................................................................................ .........................22 .0 ..........................
Outdoor wet-bulb, °F: 
Entering temperature ........................................................................................................... ......................... 1 .0 0 .3 
Leaving temperature ............................................................................................................ .........................21 .0 ..........................
External resistance to airflow, inches of water .................................................................................................... 0 .12 30 .02 
Electrical voltage, % of rdg .................................................................................................................................. 2 .0 1 .5 
Nozzle pressure drop, % of rdg .......................................................................................................................... 8 .0 ..........................
1See section 1.2, Definitions. 
2Only applies when the Outdoor Air Enthalpy Method is used. 
3Only 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 Q ˙
hkand E ˙hk(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 H1
NTest, if 
conducted.c. For heat pumps tested without 
an indoor blower installed, increase Q ˙hk(T) 
by 
and increase E ˙hk(T) by, 
where VÔ
sis 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 °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 
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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 Q ˙
hk(47) and E ˙hk(47). c. For heat pumps tested without an indoor 
blower installed, increase Q ˙hk(T) by 
and increase E ˙hk(T) by, 
where VÔ
sis 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 °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 Q ˙
hk(47) and E ˙hk(47). 
d. If conducting the cyclic heating mode 
test, which is described in section 3.8, record the average indoor-side air volume rate, VÔ, 
specific heat of the air, C
p,a(expressed on dry 
air basis), specific volume of the air at the nozzles, v
n′ (or v n), humidity ratio at the 
nozzles, W n, 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 (E ˙
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 (DP
1) exceeds the applicable section 3.1.4.4 minimum (or 
targeted) external static pressure (DP min) by 
0.03 inches of water or more. 
Determine E ˙fan,1by 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 E ˙
fan,1 
(which corresponds to DP 1): 
i. While maintaining the same test 
conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately DP
1+ (DP 1¥ DPmin). 
ii. After re-establishing steady readings for 
fan motor power and external static pressure, 
determine average values for the indoor blower power (E ˙
fan,2) and the external static 
pressure (DP 2) 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 DP
minusing linear extrapolation: 
iv. Decrease the total space heating 
capacity, Q ˙hk(T), by the quantity (E ˙fan,1¥ 
E˙fan,min ), when expressed on a Btu/h basis. 
Decrease the total electrical power, E ˙hk(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, DT (Set SS) and DT (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: 
Each time a subsequent set of temperature 
differences is recorded (if sampling more frequently than every 5 minutes), calculate F
CDusing the most recent seven sets of 
values. Continue these calculations until the 30-minute period is completed or until a value for F
CDis calculated that falls outside 
the allowable range of 0.94–1.06. If the latter occurs, immediately suspend the test and 
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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 F
CDare within the allowable range, 
save the final value of the ratio from the 30- minute test as F
CD*. 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 F
CD*= 1. 
3.8 Test procedures for the cyclic heating 
mode tests (the H0C 1, H1C, H1C 1and H1C 2 
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 C
Dvalue 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, q
cyc, as specified in section 3.5 
except for making the following changes: 
(1) When evaluating Equation 3.5–1, use 
the values of VÔ, Cp,a,vn′, (or v n), and W nthat 
were recorded during the section 3.7 steady- state test conducted at the same test conditions. 
where F CD* 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 q
cycby the 
amount calculated using Equation 3.5–3. Additionally, increase e
cycby the amount 
calculated using Equation 3.5–2. In making these calculations, use the average indoor air volume rate (VÔ
s) 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, q
cyc. 
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 q
cycand e cyc. 
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 C
Dh. 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 Q˙
hk(Tcyc) (or q cyc). The tested C Dhis 
calculated as follows: 
where, 
the average coefficient of performance during 
the cyclic heating mode test, dimensionless. 
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, T
cyc, and 
speed/capacity, k, if applicable—as specified for the cyclic heating mode test, 
dimensionless. 
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the heating load factor, dimensionless. 
Tcyc, the nominal outdoor temperature at 
which the cyclic heating mode test is 
conducted, 62 or 47 °F. Dtcyc, 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 C
Dhto the 
nearest 0.01. If C Dhis negative, then set it 
equal to zero. 
TABLE 16—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR CYCLIC HEATING MODETESTS  
Test 
operating 
tolerance1 Test 
condition 
tolerance1 
Indoor entering dry-bulb temperature,2°F .............................................................................................................. 2.0 0.5 
Indoor entering wet-bulb temperature,2°F .............................................................................................................. 1.0 ............ ............
Outdoor entering dry-bulb temperature,2°F ............................................................................................................ 2.0 0.5 
Outdoor entering wet-bulb temperature,2°F ........................................................................................................... 2.0 1.0 
External resistance to air-flow,2inches of water ..................................................................................................... 0.12 ........................
Airflow nozzle pressure difference or velocity pressure,2% of reading .................................................................. 2.0 32.0 
Electrical voltage,4% of rdg ..................................................................................................................................... 8.0 1.5 
1See section 1.2, Definitions. 
2Applies 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. 
3The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state test conducted at 
the same test conditions. 
4Applies during the interval that at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are oper-
ating, except for the first 30 seconds after compressor start-up. 
3.9 Test procedures for Frost 
Accumulation heating mode tests (the H2, 
H2 2, H2 V, and H2 1Tests). 
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, Dt
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 Q
mishould read: 
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Record the electrical energy consumed, 
expressed in watt-hours, from defrost termination to defrost termination, e
DEFk(35), as well as the corresponding elapsed time in 
hours, DtFR. 
TABLE 17—T ESTOPERATING AND TESTCONDITION TOLERANCES FOR FROST ACCUMULATION HEATING MODETESTS  
Test operating tolerance1 Test condition 
tolerance1 
Sub-interval 
H2 Sub-interval 
H2 Sub-interval 
D3 
Indoor entering dry-bulb temperature, °F .................................................................................... 2.0 44.0 0.5 
Indoor entering wet-bulb temperature, °F ................................................................................... 1.0 ........................ ............... .........
Outdoor entering dry-bulb temperature, °F ................................................................................. 2.0 10.0 1.0 
Outdoor entering wet-bulb temperature, °F ................................................................................. 1.5 ........................ 0.5 
External resistance to airflow, inches of water ............................................................................ 0.12 ........................50.02 
Electrical voltage, % of rdg ................................................................................................... ....... 2.0 ........................ 1.5 
1See section 1.2, Definitions. 
2Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a defrost cycle. 
3Applies 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. 
4For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies during the 10 minute interval that fol-
lows defrost termination. 
5Only applies when testing non-ducted heat pumps. 
3.9.1 Average space heating capacity and 
electrical power calculations. a. Evaluate average space heating capacity, 
Q˙hk(35), when expressed in units of Btu per 
hour, using: 
Where, 
VÔ= the average indoor air volume rate 
measured during Sub-interval H, cfm. 
Cp,a= 0.24 + 0.444 · W n, 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/lbm da· °F. 
vn′ = specific volume of the air-water vapor 
mixture at the nozzle, ft3/lbm mx. Wn= humidity ratio of the air-water vapor 
mixture at the nozzle, lbm of water vapor per lbm of dry air. 
Dt
FR= t2¥ t1, the elapsed time from defrost 
termination to defrost termination, hr. 
Tal(t) = dry bulb temperature of the air 
entering the indoor coil at elapsed time 
t, °F; only recorded when indoor coil 
airflow occurs; assigned the value of zero during periods (if any) where the indoor blower cycles off. 
T
a2(t) = dry bulb temperature of the air 
leaving the indoor coil at elapsed time t, °F; only recorded when indoor coil airflow occurs; assigned the value of zero during periods (if any) where the indoor 
blower cycles off. 
t
1= the elapsed time when the defrost 
termination occurs that begins the official test period, hr. 
t
2= the elapsed time when the next 
automatically occurring defrost termination occurs, thus ending the official test period, hr. 
v
n= 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
3per 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 Q ˙
hk(35) in accordance with section 
7.3.4.3 of ASHRAE Standard 37–2009. 
b. Evaluate average electrical power, 
E˙hk(35), when expressed in units of watts, 
using: 
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For heat pumps tested without an indoor 
blower installed, increase Q ˙hk(35) by, 
where VÔ
sis 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 (DP
min) by 0.03 inches of water or 
more: 1. Measure the average power consumption 
of the indoor blower motor (E ˙fan,1) and record 
the corresponding external static pressure 
(DP 1) 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 DP
1+ (DP 1¥ 
DPmin). 
3. After re-establishing steady readings for 
the fan motor power and external static 
pressure, determine average values for the indoor blower power (E ˙
fan,2) and the external 
static pressure (DP 2) 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 DP
minusing linear 
extrapolation: 
5. Decrease the total heating capacity, 
Q˙hk(35), by the quantity [(E ˙fan,1¥ E˙fan,min )· (Dt 
a/DtFR], when expressed on a Btu/h basis. 
Decrease the total electrical power, E hk(35), by the same quantity, now expressed in 
watts. 
3.9.2 Demand defrost credit. a. Assign the demand defrost credit, F
def, 
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 F
defusing, 
Where, 
Dtdef= the time between defrost terminations 
(in hours) or 1.5, whichever is greater. A 
value of 6 must be assigned to Dt defif 
this limit is reached during a Frost Accumulation test and the heat pump 
has not completed a defrost cycle. 
Dt
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 Dt
defthat 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 Dt
defbased 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, H3 2, 
H3 1and H4 2Tests). 
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 
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interval but before beginning to collect data 
to determine Q ˙hk(17) and E ˙hk(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 Q ˙
hk(17) 
and E ˙hk(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 H4
2Test. 
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 °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 °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 § 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, B
1, or B 2Test, 
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 P1
x: 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 P1
x, the 
shoulder season total off mode power. 
c. Measure P xfor 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, P
x. 
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 (P1
x) by the 
number of compressors to calculate P1, the 
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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: 
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 (P
x) from the shoulder season total off mode power (P1 x) 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: 
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 °F per hour and achieve an outdoor dry-bulb temperature of 72 °F. Maintain this temperature within ±2 °F 
for at least 5 minutes, while maintaining an indoor dry-bulb temperature of between 75 °F and 85 °F. 
b. Measure P1
x: 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 P1
x, 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 °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 °F for at least 5 
minutes, while maintaining an indoor dry- bulb temperature of between 75 °F and 85 °F. 
d. Measure P2
x: 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 P2
x, the heating 
season total off mode power. e. Measure P xfor 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, P
x 
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 (P1
x) 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: 
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 (P
x) from the shoulder season 
total off mode power (P1 x) 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: 
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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 (P2 x) 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: 
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 (P
x) from the heating season 
total off mode power (P2 x) 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: 
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, 
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where, 
Q˙ck=2(95) = the space cooling capacity 
determined from the A 2Test and 
calculated as specified in section 3.3, 
Btu/h. 
1.1 = sizing factor, dimensionless. The temperatures 95 °F and 65 °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) * EER
B 
Where, 
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PLF(0.5) = 1 ¥ 0.5 · C Dc, 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 Q ˙c(82) and 
E˙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 °F to 102 °F. Calculate SEER using Equation 4.1–1. Evaluate the quantity q
c(Tj)/N in Equation 
4.1–1 using, 
Q˙c(Tj) = the space cooling capacity of the test 
unit when operating at outdoor 
temperature, T j, 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 T
j 
to the total number of hours in the cooling season, dimensionless. a. For the space cooling season, assign n
j/ 
N as specified in Table 18. Use Equation 4.1– 
2 to calculate the building load, BL(T j). 
Evaluate Q ˙c(Tj) using, 
the space cooling capacity of the test unit at 
outdoor temperature T jif operated at the 
Cooling Minimum Air Volume Rate, Btu/h. 
the space cooling capacity of the test unit at 
outdoor temperature T jif operated at the 
Cooling Full-load Air Volume Rate, Btu/h. 
b. For units where indoor blower speed is 
the primary control variable, FP ck=1denotes 
the fan speed used during the required A 1 
and B 1Tests (see section 3.2.2.1), FP ck=2 denotes the fan speed used during the required A
2and B 2Tests, and FP c(Tj) denotes 
the fan speed used by the unit when the outdoor temperature equals T
j.For units 
where indoor air volume rate is the primary 
control variable, the three FP c’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 Q˙
ck=1(82), Q ˙ck=1(95), Q ˙ck=2(82), and 
Q˙ck=2(95). 
Where, 
PLF j= 1 ¥ CDc· [1 ¥ X(T j)], the part load 
factor, dimensionless. E˙c(Tj) = the electrical power consumption of 
the test unit when operating at outdoor 
temperature T j, W. c. The quantities X(T j) and n j/N are the 
same quantities as used in Equation 4.1.2–1. 
d. Evaluate E ˙c(Tj) using, 
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the electrical power consumption of the test 
unit at outdoor temperature T jif operated at 
the Cooling Full-load Air Volume Rate, W. 
e. The parameters FP ck=1, and FP ck=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 E˙
ck=1(82), E ˙ck=1(95), E ˙ck=2(82), and E ˙ck=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, Q ˙
ck=1(Tj), and electrical power 
consumption, E ˙ck=1(Tj), of the test unit when 
operating at low compressor capacity and outdoor temperature T
jusing, 
where Q ˙ck=1(82) and E ˙ck=1(82) are determined 
from the B 1Test, Q ˙ck=1(67) and E ˙ck=1(67) are 
determined from the F 1Test, and all four quantities are calculated as specified in section 3.3. Evaluate the space cooling capacity, Q ˙
ck=2(Tj), and electrical power consumption, E ˙ck=2(Tj), of the test unit when 
operating at high compressor capacity and outdoor temperature T
jusing, 
where Q ˙ck=2(95) and E ˙ck=2(95) are determined 
from the A 2Test, Q ˙ck=2(82), and E ˙ck=2(82), are 
determined from the B 2Test, and all are 
calculated as specified in section 3.3. 
The calculation of Equation 4.1–1 
quantities q c(Tj)/N and e c(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(T
j), 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 T
j, Q˙ck=1(Tj) ≥BL(T j). 
Where, 
Xk=1(Tj) = BL(T j)/Q˙ck=1(Tj), the cooling mode 
low capacity load factor for temperature 
bin j, dimensionless. 
PLF j= 1 ¥ CDc· [1 ¥ Xk=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 T
j 
to the total number of hours in the cooling season, dimensionless. Obtain the fractional bin hours for the cooling season, n
j/N, from Table 18. Use 
Equations 4.1.3–1 and 4.1.3–2, respectively, to evaluate Q ˙
ck=1(Tj) and 
E˙ck=1(Tj). 
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TABLE 18—D ISTRIBUTION OF FRACTIONAL HOURS WITHIN COOLING SEASON TEMPERATURE BINS 
Bin number, j Bin tempera-
ture range °F Representative 
temperature 
for bin °F Fraction of of 
total tempera-
ture 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 T j, 
Q˙ck=1(Tj) <BL(T j) <Q˙ck=2(Tj). 
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, n j/N, from Table 18. Use 
Equations 4.1.3–1 and 4.1.3–2, respectively, to evaluate Q ˙ck=1(Tj) and E ˙ck=1(Tj). Use 
Equations 4.1.3–3 and 4.1.3–4, respectively, to evaluate Q ˙
ck=2(Tj) and E ˙ck=2(Tj). 
4.1.3.3 Unit only operates at high (k=2) 
compressor capacity at temperature T jand its 
capacity is greater than the building cooling load, BL(T j) <Q˙ck=2(Tj). This section applies 
to units that lock out low compressor 
capacity operation at higher outdoor temperatures. 
where, Xk=2(Tj) = BL(T j)/Q˙ck=2(Tj), the cooling mode 
high capacity load factor for temperature 
bin j, dimensionless. PLF j= 1¥C ˙D(k=2) * [1¥Xk=2(Tj)], the part 
load factor, dimensionless. 
4.1.3.4 Unit must operate continuously at 
high (k=2) compressor capacity at 
temperature T j, BL(T j) ≥Q˙ck=2(Tj). 
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Obtain the fractional bin hours for the 
cooling season, n j/N, from Table 18. Use 
Equations 4.1.3–3 and 4.1.3–4, respectively, 
to evaluate Q ˙ck=2(Tj) and E ˙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, Q ˙
ck=1(Tj), and electrical power 
consumption, E ˙ck=1(Tj), of the test unit when 
operating at minimum compressor speed and outdoor temperature T
j.Use, 
where Q ˙ck=1(82) and E ˙ck=1(82) are determined 
from the B 1Test, Q ˙ck=1(67) and E ˙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, Q ˙
ck=2(Tj), and electrical power 
consumption, E ˙ck=2(Tj), of the test unit when operating at maximum compressor speed and 
outdoor temperature T j.Use Equations 4.1.3– 
3 and 4.1.3–4, respectively, where Q ˙ck=2(95) 
and E ˙ck=2(95) are determined from the A 2 
Test, Q ˙ck=2(82) and E ˙ck=2(82) are determined 
from the B 2Test, and all four quantities are 
calculated as specified in section 3.3. Calculate the space cooling capacity, 
Q˙ck=v(Tj), and electrical power consumption, 
E˙ck=v(Tj), of the test unit when operating at 
outdoor temperature T jand the intermediate 
compressor speed used during the section 3.2.4 (and Table 7) E
VTest using, 
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 T j, 
Q˙ck=1(Tj) ≥BL(T j). 
where, 
Xk=1(Tj) = BL(T j)/Q˙ck=1(Tj), the cooling mode 
minimum speed load factor for 
temperature bin j, dimensionless. 
PLF j= 1 ¥ CDc· [1 ¥ Xk=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 T
j 
to the total number of hours in the cooling season, dimensionless. Obtain the fractional bin hours for the 
cooling season, n
j/N, from Table 18. Use 
Equations 4.1.3–1 and 4.1.3–2, respectively, 
to evaluate Q ˙ck=l(Tj) and E ˙ck=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 T
j,Q˙ck=1(Tj) <BL(T j) <Q˙ck=2(Tj). 
where, Q ˙ck=i(Tj) = BL(T j), the space cooling capacity 
delivered by the unit in matching the building load at temperature T
j, Btu/h. The matching occurs with the unit 
operating at compressor speed k = i. 
EERk=i(Tj) = the steady-state energy efficiency 
ratio of the test unit when operating at a compressor speed of k = i and temperature T
j, Btu/h per W. Obtain the fractional bin hours for the 
cooling season, n j/N, from Table 18. For each 
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temperature bin where the unit operates at an 
intermediate compressor speed, determine the energy efficiency ratio EER
k=i(Tj) using, EERk=i(Tj) = A + B · T j+ C · T j2. For each unit, determine the coefficients A, 
B, and C by conducting the following calculations once: 
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 (Q ˙
ck=l(Tl) = BL(T 1)), °F. 
Determine T 1by 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 E
VTest, provides a space 
cooling capacity that is equal to the building load (Q ˙
ck=v(Tv) = BL(T v)), °F. 
Determine T vby 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 (Q ˙
ck=2(T2) = BL(T 2)), °F. 
Determine T 2by equating Equations 
4.1.3–3 and 4.1–2 and solving for outdoor temperature. 
4.1.4.3 Unit must operate continuously at 
maximum (k=2) compressor speed at temperature Tj, BL(T j) ≥Q˙ck=2(Tj). Evaluate 
the Equation 4.1–1 quantities 
as specified in section 4.1.3.4 with the 
understanding that Q ˙ck=2(Tj) and E ˙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 q
c(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, Q˙
ck=1(Tj), and electrical power consumption, 
E˙ck=1(Tj), of the test unit when operating at 
the cooling minimum air volume rate and outdoor temperature T
jusing the equations 
given in section 4.1.2.1. Calculate the space cooling capacity, Q ˙
ck=2(Tj), and electrical 
power consumption, E ˙ck=2(Tj), of the test unit when operating at the cooling full-load air volume rate and outdoor temperature T
j 
using the equations given in section 4.1.2.1. In evaluating the section 4.1.2.1 equations, determine the quantities Q ˙
ck=1(82) and E ˙ck=1 
(82) from the B1 Test, Q ˙ck=1(95) and E ˙ck=1 
(95) from the Al Test, Q ˙ck=2(82) and E ˙ck=2 
(82) from the B2 Test, and Q ˙ck=2(95) and 
E˙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, CD
c, as per sections 
3.2.2.1 and 3.5 to 3.5.3. Assign this same value to CD
c(K=2). c. Except for using the 
above values of Q ˙ck=1(Tj), E˙ck=1(Tj), E˙ck=2(Tj), 
Q˙ck=2(Tj), CD c, and CD c(K=2), calculate the 
quantities q c(Tj)/N and e c(Tj)/N as specified 
in section 4.1.3.1 for cases where Q ˙ck=1(Tj) 
≥ BL(T j). For all other outdoor bin temperatures, T j, calculate q c(Tj)/N and 
ec(Tj)/N as specified in section 4.1.3.3 if Q ˙ck=2 
(Tj) > BL (T j) or as specified in section 4.1.3.4 
if Q˙ck=2(Tj) ≤ BL(T j). 
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 q
c(Tj)/ 
N and e c(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, 
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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 T
j 
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(T
j)/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 T
jto 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 e
h(Tj)/N (see 4.2.5). 
Tj, the outdoor bin temperature, °F. Outdoor 
temperatures are ‘‘binned’’ such that calculations are only performed based one temperature within the bin. Bins of 5 °F are used. 
n
j/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 T
j to the total number of hours in the 
heating season, dimensionless. 
Obtain n j/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. 
F
def, the demand defrost credit described in 
section 3.9.2, dimensionless. 
BL(T j), the building space conditioning load 
corresponding to an outdoor temperature of 
T
j; 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—G ENERALIZED 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, T OD.................................. 37 27 17 5 ¥10 30 
Zero Load Temperature, T ZL........................................... 60 58 57 55 55 58 
jT j(°F) ........................................................................... Fractional Bin Hours, n j/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 
where, 
TOD, the outdoor design temperature, °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, °F Calculate the design heating requirements 
for each generalized climatic region as follows: 
For a heat pump that delivers both cooling 
and heating, 
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where, 
C = 1.3, a multiplier to provide the 
appropriate slope for the heating load 
line, dimensionless. Tzl, the zero load temperature, °F 
Q˙ck=2(95), the space cooling capacity of the 
unit as determined from the A or A 2 
Test, whichever applies, Btu/h. For a heating-only heat pump, 
where, 
C = 1.3, a multiplier to provide the 
appropriate slope for the heating load 
line, dimensionless. 
Tzl, the zero load temperature, °F 
Q˙hk(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, Q ˙hk(47) = 
Q˙h(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, Q ˙nk(47) = Q ˙nk=2(47), the 
space heating capacity determined from the 
H1 2Test. 
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. 
whichever is less; the heating mode load 
factor for temperature bin j, dimensionless. Q˙
h(Tj), the space heating capacity of the heat 
pump when operating at outdoor temperature T
j, Btu/h. E˙h(Tj), the electrical power consumption of 
the heat pump when operating at 
outdoor temperature T j, W. 
d(T j), the heat pump low temperature cut-out 
factor, dimensionless. 
PLF j= 1 ¥ C˙Dh· [1 ¥ X(T j)], the part load 
factor, dimensionless. Use Equation 4.2–2 to determine BL(T j). 
Obtain fractional bin hours for the heating 
season, n j/N, from Table 19. 
Determine the low temperature cut-out 
factor using 
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where, 
Toff, the outdoor temperature when the 
compressor is automatically shut off, °F. (If no such temperature exists, T jis 
always greater than T offand T on). 
Ton, the outdoor temperature when the 
compressor is automatically turned back on, if applicable, following an automatic 
shut-off, °F. 
Calculate Q ˙h(Tj) and E ˙h(Tj) using, 
where, 
Q˙h(47) and E ˙h(47) are determined from the H1 
Test and calculated as specified in 
section 3.7 
Q˙h(35) and E ˙h(35) are determined from the H2 
Test and calculated as specified in 
section 3.9.1 Q˙h(17) and E ˙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 °F to ¥23 °F. 
Calculate the quantities 
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 H1C
1Test and section 3.6.2. In 
addition, evaluate the space heating capacity and electrical power consumption of the heat 
pump Q ˙h(Tj) and E ˙h(Tj) using 
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 
For units where indoor blower speed is the 
primary control variable, FP hk=1denotes the 
fan speed used during the required H1 1and 
H3 1Tests (see Table 11), FP hk=2denotes the 
fan speed used during the required H1 2, H2 2, 
and H3 2Tests, and FP h(Tj) denotes the fan 
speed used by the unit when the outdoor temperature equals T j.For units where indoor 
air volume rate is the primary control 
variable, the three FP h’s are similarly defined 
only now being expressed in terms of air volume rates rather than fan speeds. 
Determine Q ˙
hk=1(47) and E ˙hk=1(47) from the 
H1 1Test, and Q ˙hk=2(47) and E ˙hk=2(47) from the H1 2Test. Calculate all four quantities as 
specified in section 3.7. Determine Q ˙hk=1(35) 
and E ˙hk=1(35) as specified in section 3.6.2; 
determine Q ˙hk=2(35) and E ˙hk=2(35) and from 
the H2 2Test and the calculation specified in 
section 3.9. Determine Q ˙hk=1(17) and E ˙hk=1(17 
from the H3 1Test, and Q ˙hk=2(17) and 
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E˙hk=2(17) from the H3 2Test. 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. 
a. Evaluate the space heating capacity and 
electrical power consumption of the heat pump when operating at low compressor 
capacity and outdoor temperature T jusing 
b. Evaluate the space heating capacity and 
electrical power consumption (Q ˙hk=2(Tj) and 
E˙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 Q˙
hk=1(62) and E ˙hk=1(62) from the H0 1Test, 
Q˙hk=1(47) and E ˙hk=1(47) from the H1 1Test, 
and Q ˙hk=2(47) and E ˙hk=2(47) from the H1 2 Test. Calculate all six quantities as specified in section 3.7. Determine Q ˙
hk=2(35) and 
E˙hk=2(35) from the H2 2Test and, if required 
as described in section 3.6.3, determine Q˙
hk=1(35) and E ˙hk=1(35) from the H2 1Test. 
Calculate the required 35 °F quantities as specified in section 3.9. Determine Q ˙
hk=2(17) 
and E ˙hk=2(17) from the H3 2Test and, if 
required as described in section 3.6.3, determine Q ˙hk=1(17) and E ˙hk=1(17) from the 
H3 1Test. Calculate the required 17 °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 T
j, 
Q˙hk=1(Tj) ≥BL(T j). 
Where, 
Xk=1(Tj) = BL(T j)/Q˙hk=1(Tj), the heating mode 
low capacity load factor for temperature 
bin j, dimensionless. PLF j= 1 ¥ CDh· [ 1 ¥ Xk=1(Tj) ], the part 
load factor, dimensionless. 
d′(T j), the low temperature cutoff factor, 
dimensionless. Determine the low temperature cut-out 
factor using 
Where, 
Toffand T onare 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) T jis 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 T
j, Q˙hk=1(Tj) < BL(T j) < 
Q˙hk=2(Tj). 
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Where, 
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, d′(T j), using Equation 4.2.3–3. 
4.2.3.3 Heat pump only operates at high 
(k=2) compressor capacity at temperature T j 
and its capacity is greater than the building heating load, BL(T j) < Q˙hk=2(Tj). This section 
applies to units that lock out low compressor capacity operation at low outdoor temperatures. 
Where, 
Xk=2(Tj)= BL(T j)/Q˙hk=2(Tj). 
PLF j= 1 ¥ C/_129(k= 2) * [1 ¥ Xk=2(Tj)] Determine the low temperature cut-out 
factor, d(T j), using Equation 4.2.3–3. 4.2.3.4 Heat pump must operate 
continuously at high (k=2) compressor 
capacity at temperature T j, BL(T j) ≥ Q˙hk=2(Tj). 
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, Q˙
hk=1(Tj), and electrical power consumption, 
E˙hk=1(Tj), of the heat pump when operating at minimum compressor speed and outdoor 
temperature T jusing 
Where, 
Q˙hk=1(62) and E ˙hk=1(62) are determined from 
the H0 1Test Q˙hk=1(47) and E ˙hk=1(47) are determined from 
the H1 1Test, and all four quantities are calculated as 
specified in section 3.7. 
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Evaluate the space heating capacity, 
Q˙hk=2(Tj), and electrical power consumption, 
E˙hk=2(Tj), of the heat pump when operating 
at maximum compressor speed and outdoor 
temperature T jby 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 
Q˙
hk=2(47) and E ˙hk=2(47) from the H1 2Test 
and the calculations specified in section 3.7. Determine Q ˙hk=2(35) and E ˙hk=2(35) from the 
H2 2Test and the calculations specified in 
section 3.9 or, if the H2 2Test is not 
conducted, by conducting the calculations 
specified in section 3.6.4. Determine Q˙
hk=2(17) and E ˙hk=2(17) from the H3 2Test 
and the calculations specified in section 3.10. 
If H4 2test is conducted, evaluate the space 
heating capacity, Q ˙hk=2(Tj), and electrical power consumption, E ˙hk=2(Tj), of the heat 
pump when operating at maximum 
compressor speed and outdoor temperature T
jby using the following equation instead of 
Equations 4.2.2–3 and 4.2.2–4. Determine the quantities Q ˙
hk=2(Tl) and E ˙hk=2(Tl) from the 
H4 2Test and the calculations specified in 
section 3.7. 
Where Tlis the outdoor temperature where 
the H4 2test is conducted. Calculate the space heating capacity, 
Q˙hk=v(Tj), and electrical power consumption, 
E˙hk=v(Tj), of the heat pump when operating at outdoor temperature T jand the 
intermediate compressor speed used during 
the section 3.6.4 H2 VTest using 
Where, Q ˙hk=v(35) and E ˙hk=v(35) are determined from 
the H2 VTest and calculated as specified 
in section 3.9. Approximate the slopes of the k=v intermediate speed heating capacity and electrical power input curves, M
Qand M E, as follows: 
Use Equations 4.2.4–1 and 4.2.4–2, 
respectively, to calculate Q ˙hk=1(35) and 
E˙hk=1(35). The calculation of Equation 4.2–1 
quantities e h(Tj)/N and RH(T j)/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. 
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and d(T j) is evaluated using Equation 4.2.3– 
3 while, 
Q˙hk=i(Tj) = BL(T j), the space heating capacity 
delivered by the unit in matching the 
building load at temperature (T j), 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 T
j, 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 · T j+ C · T j2. 
For each heat pump, determine the 
coefficients A, B, and C by conducting the 
following calculations once: 
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 (Q ˙
hk=1(T3) = BL(T 3)), °F. Determine T 3by equating Equations 
4.2.4–1 and 4.2–2 and solving for 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 H2
VTest, 
provides a space heating capacity that is equal to the building load (Q ˙hk=v(Tvh) = 
BL(T vh)), °F. Determine T vhby equating 
Equations 4.2.4–3 and 4.2–2 and solving for outdoor temperature. T
4, 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 (Q ˙
hk=2(T4) = BL(T 4)), °F. 
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Determine T 4by equating Equations 4.2.2– 3 (k=2) and 4.2–2 and solving for outdoor 
temperature. 
For multiple-split heat pumps (only), the 
following procedures supersede the above requirements for calculating COP hk=i(Tj). For 
each temperature bin where T 3>Tj>Tvh, 
4.2.4.3 Heat pump must operate 
continuously at maximum (k=2) compressor speed at temperature T j, BL(T j) ≥Q˙hk=2(Tj). 
Evaluate the Equation 4.2–1 quantities 
as specified in section 4.2.3.4 with the 
understanding that Q ˙hk=2(Tj) and E ˙hk=2(Tj) 
correspond to maximum compressor speed operation and are derived from the results of the specified section 3.6.4 tests. If H4
2test is 
conducted in place of H1 2, evaluate Q ˙hk=2(Tj) and E ˙hk=2(Tj) using the following equation 
instead of equations 4.2.2–3 and 4.2.2–4. 
Where, T Lis the ambient dry bulb 
temperature where H4 2test 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 
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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, T
j, 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/lbm
da· °F) from the results 
of the H1 Test using: 
Where VÔ
s, VÔ
mx, v′ n(or v n), and W nare 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, 
Evaluate e h(Tj/N), RH(T j)/N, X(T j), PLF j, 
and d(T j) 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 T
o(Tj) is equal to or greater than T CC 
(the maximum supply temperature 
determined according to section 3.1.9), determine Q ˙
h(Tj) and E ˙h(Tj) as specified in 
section 4.2.1 (i.e., Q˙h(Tj) = Q˙hp(Tj) and E ˙hp(Tj) = E˙hp(Tj)). Note: Even though T o(Tj) ≥Tcc, 
resistive heating may be required; evaluate Equation 4.2.1–2 for all bins. 
Case 2. For outdoor bin temperatures 
where T
o(Tj) >T cc, determine Q ˙h(Tj) and E ˙h(Tj) 
using, 
NOTE: Even though T o(Tj) <T 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, T
j, 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/lbm
da· °F) from the results of the H1 2 
Test using: 
Cp,da= 0.24 + 0.444 * Q n Where VÔ
S, VÔ
mx, v′ n(or v n), and W nare 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, 
Evaluate e h(Tj)/N, RH(T j)/N, X(T j), PLF j, 
and d(T j) as specified in section 4.2.1 with 
the exception of replacing references to the 
H1C Test and section 3.6.1 with the H1C 1 
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 T
o(Tj) is equal to or greater than T CC 
(the maximum supply temperature determined according to section 3.1.9), determine Q ˙
h(Tj) and E ˙h(Tj) as specified in section 4.2.2 (i.e. Q˙h(Tj) = Q˙hp(Tj) and E ˙h(Tj) 
= E˙hp(Tj)). Note: Even though T o(Tj) ≥TCC, 
resistive heating may be required; evaluate Equation 4.2.1–2 for all bins. 
Case 2. For outdoor bin temperatures 
where T
o(Tj) <T CC, determine Q ˙h(Tj) and 
E˙h(Tj) using, 
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Note: Even though T o(Tj) <T 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, T
j, 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/lbm
da· °F) from the results of the H1 1 
Test using: 
Where VÔ
s, VÔ
mx, v′ n(or v n), and W nare 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, 
Repeat the above calculations to determine 
the mass flow rate (m ˙dak=2) and the specific 
heat of the indoor air (C p,dak=2) when operating at high capacity by using the 
results of the H1 2Test. 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, 
Evaluate e h(Tj)/N, RH(T j)/N, Xk=1(Tj), and/ 
or Xk=2(Tj), PLF j, and d′(T j) or d″(T j) 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 T
ok=1(Tj) is equal to or greater than T CC 
(the maximum supply temperature determined according to section 3.1.9), determine Q ˙
hk=1(Tj) and E ˙hk=1(Tj) as specified in section 4.2.3 (i.e., Q˙hk=1(Tj) = Q˙hpk=1(Tj) 
and E ˙hk=1(Tj) = E˙hpk=1(Tj). 
Note: Even though T ok=1(Tj) ≥TCC, resistive 
heating may be required; evaluate RH(T j)/N 
for all bins. 
Case 2. For outdoor bin temperatures 
where T ok=1(Tj) <T CC, determine Q ˙hk=1(Tj) 
and E ˙hk=1(Tj) using, 
Note: Even though T ok=1(Tj) ≥Tcc, 
additional resistive heating may be required; 
evaluate RH(T j)/N for all bins. 
Case 3. For outdoor bin temperatures 
where T ok=2(Tj) is equal to or greater than 
TCC, determine Q ˙hk=2(Tj) and E ˙hk=2(Tj) as specified in section 4.2.3 (i.e., Q˙hk=2(Tj) = 
Q˙hpk=2(Tj) and E ˙hk=2(Tj) = E˙hpk=2(Tj)). 
Note: Even though T ok=2(Tj) <T CC, resistive 
heating may be required; evaluate RH(T j)/N 
for all bins. Case 4. For outdoor bin temperatures 
where T ok=2(Tj) <T CC, determine Q ˙hk=2(Tj) 
and E ˙hk=2(Tj) using, 
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Note: Even though T ok=2(Tj) <T cc, 
additional resistive heating may be required; 
evaluate RH(T j)/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 
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 °F ≤ T ≤ 65 °F; At the high (k=2) compressor capacity, the outdoor 
temperature range of operation is 20 °F ≤ T 
≤ 50 °F; At the booster (k=3) compressor 
capacity, the outdoor temperature range of operation is ¥20 °F ≤ T ≤ 30°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 Q˙
hk=1(Tj) and E ˙hk=1(Tj)) In evaluating the 
section 4.2.3 equations, Determine Q ˙hk=1(62) 
and E ˙hk=1(62) from the H0 1Test, Q ˙hk=1(47) 
and E ˙hk=1(47) from the H1 1Test, and 
Q˙hk=2(47) and E ˙hk=2(47) from the H1 2Test. 
Calculate all four quantities as specified in section 3.7. If, in accordance with section 3.6.6, the H3
1Test is conducted, calculate 
Q˙hk=1(17) and E ˙hk=1(17) as specified in 
section 3.10 and determine Q ˙hk=1(35) and 
E˙hk=1(35) as specified in section 3.6.6. b. Evaluate the space heating capacity and 
electrical power consumption (Q ˙hk=2(Tj) and 
E˙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 Q˙
hk=1(62) and E ˙hk=1(62) from the H0 1Test, 
Q˙hk=1(47) and E ˙hk=1(47) from the H1 1Test, 
and Q ˙hk=2(47) and E ˙hk=2(47) from the H1 2 
Test, evaluated as specified in section 3.7. Determine the equation input for Q ˙
hk=2(35) 
and E ˙hk=2(35) from the H2 2,evaluated as 
specified in section 3.9.1. Also, determine Q˙
hk=2(17) and E ˙hk=2(17) from the H3 2Test, 
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 
Determine Q ˙hk=3(17) and E ˙hk=3(17) from the 
H3 3Test and determine Q ˙hk=2(2) and E ˙hk=3(2) 
from the H4 3Test. Calculate all four 
quantities as specified in section 3.10. Determine the equation input for Q ˙hk=3(35) 
and E ˙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 T j, 
Q˙hk=1(Tj) ≥BL(T j)., and the heat pump permits 
low compressor capacity at T j.Evaluate the 
quantities 
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using Eqs. 4.2.3–1 and 4.2.3–2, respectively. 
Determine the equation inputs Xk=1(Tj), PLF j, 
and d′(T j) as specified in section 4.2.3.1. In 
calculating the part load factor, PLF j, use the 
low-capacity cyclic-degradation coefficient CDh, [or equivalently, C Dh(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 T j and its capacity is greater than or equal to the 
building heating load, BL(T j) <Q˙hk=2(Tj). 
Evaluate the quantities 
as specified in section 4.2.3.3. Determine the 
equation inputs Xk=2(Tj), PLF j, and d′(T j) as 
specified in section 4.2.3.3. In calculating the 
part load factor, PLF j, use the high-capacity cyclic-degradation coefficient, C Dh(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 T j and its capacity is greater than or equal to the 
building heating load, BL(T j) ≤Q˙hk=3(Tj). 
where 
Xk=3(Tj) = BL(T j)/Q˙hk=3(Tj) and PLF j= 1 ¥ 
CÆ
≤h (k = 3) * [1 ¥ Xk=3(Tj) 
Determine the low temperature cut-out 
factor, d′(T j), using Eq. 4.2.3–3. Use the booster-capacity cyclic-degradation 
coefficient, C Dh(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 T j, Q˙hk=1(Tj) <BL(T j) 
<Q˙hk=2(Tj). Evaluate the quantities 
as specified in section 4.2.3.2. Determine the 
equation inputs Xk=1(Tj), Xk=2(Tj), and d′(T j) 
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 T
j, Q˙hk=2(Tj) <BL(T j) 
<Q˙hk=3(Tj). 
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, d′(T j), using Eq. 
4.2.3–3. 
4.2.6.6 Heat pump only operates at low 
(k=1) capacity at temperature T jand its capacity is less than the building heating load, BL(T
j) > Q˙hk=1(Tj). 
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Where the low temperature cut-out factor, 
d′(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) > Q ˙hk=2(Tj). Evaluate the 
quantities 
as specified in section 4.2.3.4. Calculate d″(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(T
j) > Q˙hk=3(Tj). or the system 
converts to using only resistive heating. 
Where d″(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 T
j, set d′(T j) 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 e
h(Tj)/N and 
RH(T j)/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, 
Q˙
hk=1(Tj), and electrical power consumption, 
E˙hk=1(Tj), of the heat pump when operating at 
the heating minimum air volume rate and outdoor temperature T
jusing Eqs. 4.2.2–3 
and 4.2.2–4, respectively. Use these same equations to calculate the space heating capacity, Q ˙
hk=2(Tj) and electrical power 
consumption, E ˙hk=2(Tj), of the test unit when 
operating at the heating full-load air volume 
rate and outdoor temperature T j. In 
evaluating Eqs. 4.2.2–3 and 4.2.2–4, determine the quantities Q ˙
hk=1(47) and 
E˙hk=1(47) from the H1 1Test; determine Q ˙hk=2 
(47) and E ˙hk=2(47) from the H1 2Test. Evaluate 
all four quantities according to section 3.7. Determine the quantities Q ˙
hk=1(35) and 
E˙hk=1(35) as specified in section 3.6.2. 
Determine Q ˙hk=2(35) and E ˙hk=2(35) from the 
H2 2Frost Accumulation Test as calculated 
according to section 3.9.1. Determine the quantities Q ˙
hk=1(17) and E ˙hk=1(17) from the 
H3 1Test, and Q ˙hk=2(17) and E ˙hk=2(17) from 
the H3 2Test. 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, CD
h, as per sections 
3.6.2 and 3.8 to 3.8.1. Assign this same value to CD
h(k = 2). c. Except for using the above values of 
Q˙hk=1(Tj), E ˙hk=1(Tj), Q ˙hk=2(Tj), EÔ
hk=2(Tj), CD h, 
and CD h(k = 2), calculate the quantities 
eh(Tj)/N as specified in section 4.2.3.1 for 
cases where Q ˙hk=1(Tj) ≥ BL(T j). For all other 
outdoor bin temperatures, T j, calculate e h(Tj)/ 
N and RH h(Tj)/N as specified in section 
4.2.3.3 if Q ˙hk=2(Tj) > BL(Tj) or as specified in 
section 4.2.3.4 if Q ˙hk=2(Tj) ≤ BL(T j). 
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 e
h(Tj)/N and 
RH(T j)/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, P W,OFF , with the following 
equation: 
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 · SSH; and the off mode 
energy consumption of a CAC, only, for the heating season, E2, using: E2 = P2 · 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 °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 °F to ¥23 °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—R EPRESENTATIVE COOLING AND HEATING LOADHOURS AND THE CORRESPONDING SET OF SEASONAL HOURS  
FOREACHGENERALIZED CLIMATIC REGION  
Climatic region Cooling load 
hours 
CLH R Heating load 
hours 
HLH R Cooling 
season hours 
CSH R Heating 
season hours 
HSH R Shoulder 
season hours 
SSH R 
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 
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TABLE 20—R EPRESENTATIVE COOLING AND HEATING LOADHOURS AND THE CORRESPONDING SET OF SEASONAL HOURS  
FOREACHGENERALIZED CLIMATIC REGION —Continued 
Climatic region Cooling load 
hours 
CLH R Heating load 
hours 
HLH R Cooling 
season hours 
CSH R Heating 
season hours 
HSH R Shoulder 
season hours 
SSH R 
VI .......................................................................................... 200 2,750 561 6,258 1,941 
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 · CLH. 
TABLE 21—F RACTIONAL BINHOURS FOR THE SHOULDER SEASON HOURS FOR ALLREGIONS  
Tj(°F) Fractional bin hours 
Air conditioners Heat pumps 
72 ................................................................................................................................................................... 0 .333 0.167 
67 ................................................................................................................................................................... 0 .667 0.333 
62 ................................................................................................................................................................... 0 0.333 
57 ................................................................................................................................................................... 0 0.167 
4.3.4 For air conditioners, the annual off 
mode energy consumption, E TOTAL , is: E TOTAL  
= E1 + E2. 
4.3.5 For heat pumps, the annual off 
mode energy consumption, E TOTAL , 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 (APF A) for a particular location and for each standardized 
design heating requirement. 
Where, 
CLH A= the actual cooling hours for a 
particular location as determined using 
the map given in Figure 2, hr. 
Q˙ck(95) = the space cooling capacity of the 
unit as determined from the A or A 2 
Test, whichever applies, Btu/h. HLH A= 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·h. 
HSPF = the heating seasonal performance 
factor calculated as specified in section 
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4.2 for the generalized climatic region 
that includes the particular location of interest (see Figure 1), Btu/W·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 (APF
R) 
for each generalized climatic region and for 
each standardized design heating requirement. 
Where, 
CLH R= the representative cooling hours for 
each generalized climatic region, Table 
22, hr. HLH R= 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, Q ˙
ck(95), DHR, and C are the 
same quantities as defined in section 4.4.1. Figure 1 shows the generalized climatic regions. 
TABLE 22—R EPRESENTATIVE COOLING AND HEATING LOADHOURS FOR EACHGENERALIZED CLIMATIC REGION  
Region CLH R HLH R 
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. 
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4.6 Calculations of the SHR, which 
should be computed for different equipment configurations and test conditions specified 
in Table 23. 
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EP09NO15.440</GPH>tkelley on DSK3SPTVN1PROD with PROPOSALS2Figure !-Heating Load Hours (HLHA) for the United States 
Figure 2-Cooling Load Hours (CLHA) for the United States 69455 Federal Register / Vol. 80, No. 216 / Monday, November 9, 2015 / Proposed Rules 
TABLE 23 A PPLICABLE TESTCONDITIONS FORCALCULATION OF THE SENSIBLE HEATRATIO 
Equipment configuration Reference 
Table No. of 
Appendix M SHR computation with results 
from Computed values 
Units Having a Single-Speed Compressor and a Fixed-Speed Indoor 
blower, a Constant Air Volume Rate Indoor blower, or No Indoor 
blower.4 B Test ........................................... SHR(B). 
Units Having a Single-Speed Compressor That Meet the Section 
3.2.2.1 Indoor Unit Requirements.5 B2 and B1 Tests ........................... SHR(B1), SHR(B2). 
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: 
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, 
Where Q ˙ck(T) and E ˙ck(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., EER
A2) to differentiate 
among the resulting EER values. 
■12. Section 430.32 is amended by 
revising paragraph (c) to read as follows: § 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: 
Product class Seasonal 
energy 
efficiency ratio 
(SEER) Heating 
seasonal 
performance 
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 conditioners ............................................................................................. 12 ........................
(vi)(B) Space-constrained products—heat pumps .................................................................................. ................ 12 7.4 
(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 
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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°F dry bulb outdoor temperature) not 
less than the following: Product class Energy 
efficiency ratio 
(EER) 
(i) Split-system rated cooling 
capacity less than 45,000 
Btu/hr ................................. 12.2 
(ii) Split-system rated cooling 
capacity equal to or great-er than 45,000 Btu/hr ........ 11.7 
(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: Product class Average off 
mode power 
consumption 
PW,OFF  
(watts) 
(i) Split-system air condi-
tioners ............................... 30 
(ii) Split-system heat pumps 33 
(iii) Single-package air condi-
tioners ............................... 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 
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