## Tuesday 

# October 7, 1986



# Part II

. 

# ....

Department of Energy

Office of Conservation and Renewable Energy

10 CFR Part 430 Energy Conservation Program for Consumer Products; Test Procedures for Central Air Conditioners, Including Heat Pumps; Proposed Rule and Public Hearing

### 35736 

### Federal Register 

## I Vol. 51. No. 194 

## I Tuesday. October 7. 1986 

## I Proposed Rules

DEPARTMENT OF ENERGY

Office of 

### Conservation and Renewable Energy



### 10CFA 

### Part430 (Docket

### No. CAS-RM-7I-102) 

### Energy Conservation Programfor Consumer Products; Proposed Rulemaklng and Public Hearing Regarding T

.. t Procedu,.. for Centra. Air Conditioners, Including Heat Pump.

AGENCY: 

### Office ofConservation and Renewable Energy. DOE.
ACTION: 

### Proposed rule and public hearing.

SUMMARY:

### The Department ofEnergy (DOE) hereby proposes to amend the test procedures for central air ' conditioners. including heat pumps. Test procedures are one part ofthe energy conservation program for consumer products established pursuant to the Energy Policy and Conservation Act. as amended by the National Energy Conservation Policy Act. Among other program elements. the legislation requires that standard methods of testing be prescribed for covered products.

The purpose oftoday's notice is 'hreefold. First, to incorporate. by reference. three commercial standards into the test procedures. The standards

are the American National Standards Institute (ANSI) and American Society ofHeating. Refrigerating, and AirConditioning Engineers. Inc. (ASHRAE) Standard 116-1983. the Air-Conditioning and Refrigeration Institute (ARI) Standard 210/240-84. and the ANSI/ARI Standard 325-85. Second. to prescribe a rating procedure for estimating efficiency ratings for untested combinations ofsplit-system central air conditioners in lieu oflaboratory testing. Third. to expand the coverage ofthe test procedures to address innovative designs, including ground water-source heat pumps. earth-coupled heat pumps. split-type ductless systems and variablespeed central air conditioners.
DATES: 

### Written comments (7 copies) in response to this notice must be received

. by December 8.1986; requests to speak

at the public hearing must be received by November 7. 1986; statements (7 copies) must be submitted by November 10. 1986; the public hearing will be held

on November 12,1986, at 9:30 a.m. ADDRESSES: 

### Written comments. requests to speak at the public hearing. and copies ofstatements ofeach speaker are**~** 

### be submitted to: U.S. Department of Energy, Office ofConservation and Renewable

### Energy. Office ofHearinga and

### Dockets. Central Air

### Conditioner TestProcedures. Docket No. CA8-RM79-102. Room 68-025. Forrestal Building. 1000 Independence Avenue. SW •• Washington. DC 20585. (202) 252-8319.

Thepublic hearing will 

### be held at Room 1E-24S. Forrestal Building. 1000 IndependenceAvenue. SW •• Washington. DC 20585.

Copies ofthetranscript ofthe public hearing. the technical support documents and the public comments received may

### be obtained at the DOE Freedom ofInformation Reading Room. Room 1E-190. 1000 Independence Avenue. SW .• Washington. DC 20585. (202) 252-5969.

FOR FURTHER INFORMATION CONTACT: 

### Michael

## J. McCabe. U.S. Department of

Energy. Office ofConservation and Renewable Energy. Forrestal Building. Mail Station, CE-132. 1000 Independence Avenue. SW •• Washington. DC 20585. (202) 252-9127 Eugene Margolis. Esq.• U.S. Department

ofEnergy. Office ofGeneral Counsel, Forrestal Building. Mail Station. GC12. 1000 Independence Avenue. SW .• Washington. DC 20585, (202) 252-9513 U.S. Department ofEnergy. Office of

Hearings and Dockets. Forrestal Building, Room 6b-025. 1000 Independence Avenue. SW.• Washington. DC 20585. (202) 252-9319.

SUPPLEMENTARY INFORMATION:


### I. Background

The energy conservation program for

consumer products was established pursuant to Title Ill. Part B ofthe Energy Policy and Conservation Act (EPCA) (Pub. L. 94-163). Subsequently. EPCA

was amended by the National Energy Conservation Policy Act (NECPA) (Pub. L. 95-619). Among other program elements. section 323 of the EPCA as amended requires that standard methods oftesting be prescribed for covered products. including central air conditioners and heat pumps. Test procedures appear at 10 CFR Part430. Subpart B.

Test procedures for evaluating the cooling performance of air-source central air conditioners were initially issued by DOE on November 21. 1977 (42 FR 60150, November 27. 1977). A correction notice amending this notice

was issued by DOE on May 31, 1978 (43 FR 24268, June 5, 1978). Test procedures for evaluating the heating performance ofair-source heat pumps as well as amending the test procedures for central air conditioners were issued by DOE on December 10. 1979 (44 FR 76700. December 27, 1979). On March 15. 1985. DOE issued a Notice ofInquiry to solicit comments conceming a rating method for determining efficiency ratings for untested combinations ofsplit-system central airconditioners in lieu of laboratory testing ofthe units (50 FR 13042. 

### April 2, 

### 1985).

There are

### threepurposes for today's notice. Firat. to incorporate three commercial standards into the central airconditioner testprocedures. The standards areANSI/ASHRAE Standard 116-1983. ARI Standard 210/240-84 and ANSI/ARI Standard 325-85. Second. to prescribe a ratingmethod for estimating efficiency ratings for untested

. combinations ofsplit-system central air conditioners in lieu oflaboratory testing. Lastly. DOE is proposing to expand the coverage ofthe test procedures to address innovative designs. including ground water-source heat pumps. earthcoupled heat pumps. split-type ductless systems and variable-speed central air conditioners.

This third area includes variablespeed central air conditioners and addresses the 1981 exception from the central air conditioner test procedures granted by the DOE Office ofHearings and Appeals (OHA) to York Division Unitary Products (York) for its variablespeed heat pump. 

### FederalEnergy Guidelines. 7 DOE**~** 

### 81.209. In 1983, OHA extended the exception to BorgWarner Central Environmental Systems (Borg-Warner), formerly York. 

### Federal Energy Guidelines. 10 DOE**~** 

### 81.206. The two exceptions specify an alternative test procedure for evaluating variablespeed heat pumps. In 

### 1986. the Carrier Corporation (Carrier) petitioned the Department for a test procedure waiver for its variable-speed heat pump (February 14, 1986. 51 FR 5587). Carrier. in its petition. proposed as alternative test procedure which was different from the Borg-Warner approach. Today's notice proposes alternative test procedures for variable-speed heat pumps based upon the exception granted to Borg-Warner and the waiver granted to Carrier.

II. Discussion

The central air conditioner is a
consumer product which utilizes the mechanical refrigerator cycle to provide heating and/or cooling. The central air conditioner consists ofa compressor(s).

an indoor conditioning coil and refrigerant-to-outdoor-air heat exchanger. The current test procedure provides for a controlled laboratory environment for measuring energy consumption ofair-source central air conditioners. including heat pumps. The current test method for cooling performance consists oftwo steady-

### Federal Register 

## I Vol. 51. No. 194 

## I Tuesday. October 7. 1986 

## I Proposed Rules 35737

state**wet~coil** tests. and two cyclic 

### drycoil tests for determining cyclic performance. 111e current test method for beatingperformance consists offour
tests to evaluate: the steady-state efficiency. energy lost due to defrosting. the effect ofcycling the unit and the efficiency at low temperatures. 111e cycling tests require simulating the cyclicbehaviorofcentral air conditioners. Because the cyclic tests

are difficult to perform. the current test procedures provide for an assigned degradation coefficent. CD. whichmay beused in lieu ofconducting the cyclic
tests. 111e assigned coefficient is0.25 for both heating and cooling. Furthermore. the current test procedure provides for the use ofcomputer simulation or engineering analysis ofthe efficiency of condensor-evaporatorcoil combinations other than the combination likely to have the highest sales volume ofretail sales.

### See 1 430.23(m). Manufacturers who chose to use computer simulation

orengineering analysis must submit to DOE a written document describing the method used.

111e current test procedure applies to air-source central air conditioners. and does not address ground water-source heat pumps. earth-coupled heat pumps. split-type ductless systems and variablespeed central air conditioners. At DOE's request, the National Bureau of Standards (NBS) evaluated existing test methods for "measuring energy consumption ofcentral air conditioners. Based upon NBS recommendations, DOE is proposing to add Appendix Ml
to the test procedures for central air conditioners. The new Appendix is based on ANSI!ASHRAE Standard 116- 1983 and ARI Standard**210/24~.** A rating method for estimating efficiency ratings for untested combinations of split-system central air conditioners is included in section 4.6.1 ofAppendix Ml oftoday's proposal. Appendix M will remain in effect for 2 years allowing currently tested units to continue to be rated without having to retest.

Under today's notice, central air conditioners could be tested during a transition period of24 months by using either Appendix M or Appendix M1. After that period, only Appendix Ml would be used for testing central air conditioners. Further details ofthe transition period are discussed in paragraph h oftoday's notice.

Ratings for untested combinations of split-system central air conditioners would be determined by the standardized rating method in section 4.6.1 ofAppendix M1 oftoday's notice. No other method would be used unless a manufacturerreceived DOE's approval to use an alternativerating method under 1430.23 (m)(S). Furtherdetails concerning alternativerating methods

arediscussed laterin this notice. "

111e test procedures proposed today incorporate inpart. three commercial standards to measure the efficiency and capacityofcentral airconditioners. 111e three commercial standards are: ANSI! 

### ASHRAE Standard 116-1983. 

### ARI Standard 210/240-84 and ANSI/

### ARI Standard 325-63.

Pursuant to section 301 ofthe " Department ofEnergy OrganizationAct (Pub. 

### L 95-91). DOE is required to " comply with section 32 ofthe Federal Energy Administration Act of 1974 (FEA Act) (Pub. 

### L 93-275). as amended by section 9 ofthe Federal Energy Administration AuthorizationAct of 1977 (Pub. 

### L 95-70).

Sections 32 (a). (b). and (cJ ofthe FEA Act provide that:

(aJ 

### Ifany proposed rule by the Secretary contains any commercial standards, orspecifically authorizes or requires the use ofany such standards. then any general notice ofthe proposed rulemaking shaIl-

(1) Identify. by name. the organization which promulgated such standards; and

(2) State whether or not, in the judgment ofthe Secretary, such organization complied with the requirements ofsubsection (b) in the promulgation ofsuch standards.

(b) An organization complied with the requirements of this subsection in promulgating any commercial standards if-

(1) It gives interested persons adequate notice of the proposed promulgation of the standards and an opportunity to participate in the promulgation process through the presentation of their views in hearing or meetings which are open to the public:

(2) The membership of the organization at the time of the promulgation of the standards is sufficiently balanced so as to allow for the effective representation of all interested persons:

(3) Before promulgating such standard, it makes available to the public any records or proceedings ofthe organization, and any documents. letters, memorandums, and materials relating to such standards: and

(A) Obtain a reconsideration ofany action taken by the organization relating
to the promulgation of such standards, and

(B) Obtain a review of the standards (including a review of the basis or adequacy of such standards).

(c) The Secretary shall not incorporate within any rule, nor prescribe any rule specifically authorizing orrequiring the

use of. any commercial standards unless behas consulted with the Attorney General and the Chairman ofthe FederalTrade Commission concerning the impact ofsuch standards on competition and neither such individual recommends against such incorporation "oruse.

111e findings required ofDOEby section 32 ofthe FEA Act serve to alert the public andDOEregarding the use and background ofcommercial standards in a proposal and. through the "rulemaking process. allow interested

persons to make known their views regarding the appropriateness ofthe use ofanyparticular commercial standard in a proposed rulemaking.

DOEhas evaluated ANSI/ ASHRAE "Standard 11&-1983. ARI Standard 2101 240-84 and ANSI/

### ARI Standard 325-83 with regard to compliance with section 32(b). Itis the judgment ofDOE that these three standards do not fully comply with the requirements ofsection 32(b), in that these standards were not developed in a mannerwhich fully provided for publicparticipation,
comment and review

Furthermore, as required by section 32(c) ofthe FEA Act, DOE will consult with the Attorney General and the Chairman ofthe Federal Trade Commission concerning the impact of these standards on competition, prior to prescribing final test procedures.



### a. ANSI/ASHRA.EStandard 116-1983. 

### ARIStandard210/240-84 

### andANSI! ARIStandard325-83

Subsequent to DOE's 1979 final rule, manufacturers identified a number of problems with the test procedure. As a result. ASHRAE established a Standard Project Committee (SPC) for the purpose ofdeveloping an industry consensus test method which addressed these problems. The most significant change

was to revise the test method for measuring the degradation effect caused by cycling of the unit.

The DOE test procedure prescribes a damper method. while the ASHRAE procedure prescribes a continuous air method. The continuous air method is a
more repeatable test because the test initiates each cycle with no temperature differential across the indoor coil. 

### See "Seasonal Performance ofAir Conditioners-Experimental Analysis of the DOETest Procedures Set Up Measurement Errors for Unitary Air Conditioners and Heat Pumps", HL 82- 2T, Purdue University, May 1982. The damper method results in a temperature differential across the indoor coil that

can vary from cycle to cycle, which

### 35738 

### Federal Register 

## I Vol. 51, No. 194 

## I Tuesday. October 7. 1986 

## I Proposed Rules

results in greater variability in test results. Forthese reaions:NBS recommended using the continuous air method. DOE has reviewed these recommendations and agrees that the continuous air method is a more repeatable test andresults in less variability in ratings. There are additional advantages in the continuous

_ airmethod. including a simpler test setup since no damper arrangement is required and less chance ofhaving testing conditions drift over time due to cracks and openings in the damper. Consequently. DOE is proposing that the continuous airmethod, as prescribed in ANSI/ASHRAE Standard**11~1983** 

### be used in conducting Test D.

One issue in proposing the continuous air method is to determine appropriate times for measuring the output capacity and input power during the cyclic tests. As with the existing DOE procedures, the ARI Standard 210/240-84 specifies that these testsbe conducted by cyc1ying the unit 6 minutes on and 24 minutes ofC. According to the ARI standard, the power shall be measured for six minutes while the capacity shall be measured Cor eight minutes. DOE believes that the ARI method of measuring power and capacity oC 

### different time periods does not accurately describe the perCormance observed in the field. Consequently. DOE is proposing that both power and capacity should be measured for six minutes. See 

### 3.1.1 ofAppendix Ml of todav's notice.**Al~o.** ANSI!ASHRAE Standard**11~** 1983 uses a bin method for determining the SEER for single-speed units. The DOE test procedure specifies a simpler but less accurate approach. consisting oC



### a single equation Cor determining the SEER for single-speed units. The simpler approach was prescribp.d by DOE to reduce testing burden. The current DOE test procedure specifies a bin method for all other types ofcentral air conditioners. including two speed units. DOE believes that results from the bin approach are more accurate. and are not burdensome. Therefore. DOE is proposing that the SEER for single-speed units should be determined by the bin methods prescribed in ASHRAE Standard**11~1983.**



### Finally. the ANSI/ASHRAE Standard**11~1983** 

### differs from the existing procedures by not including enhancement credit for "demand defrost" control systems. Where the existing procedures assign a fixed credit for units with this type ofcontrol system

no such credit is available in the ANSI/ ASHRAE Standard**11~1983** 

### procedures. The existing procedures assigned this credit to compelUlate for improved performance Dot meaBUred inthe Frost AccumulationTest, SpecficalJy. the system capacitymeasured during the Frost AccumulationTestis increased by

seven percent to account for the seasonalperformance improvemenL The introduction ofthis enhancementfactor improves HSPF by approximatelyfour percent which agreed with the available field data at 

### the time the procedures

wereprescribed.

DOE believes it 

### appropriate to continue enhancement creditfor "demand defrost" control systems and is therefore, including such a creditin today's proposal. However, today's proposed credit differs from that in the existing procedures, where inlieu ofa single seven percent capacity enhancement credit, today's proposal would include an HSPF enhancement credit which is prorated linearly based

on the number ofdefrost cycles saved by the control. This improved method would result in the same enhancement for units that were the basis ofthe existing procedures (e.g., single speed, poor frosting performance, etc.); however, higher efficiency units (e.g. variable speed, improved frosting performance. etc.) would receive less enhancement. DOE believes this adjustment is appropriate since much of the improved performance due to demand defrost controls on high efficiency units is measured in the Frost Accumulation Test. In 

### fact, ifthe unit does not defrost during laboratory testing, the maximum improvement for defrost controls is reflected in the test procedures and no further enhancement is deserved. In 

### such a case, today's proposal would assign an enhancement factor ofunity (Le. no additional credit for demand defrost controls).

h. Degradation Coefficient



### The test procedure included tests for measuring the degradation effect caused by cycling of the unit (cyclic tests). In 

### order to reduce the burden of testing on manufacturers with limited capability for testing. an assigned degradation coefficient. CDo 

### may be used in lieu of conducting the cyclic tests.

For cooling, the DOE test procedures permits manufacturers to conduct cycling tests (Tests C and D) to determine the actual value ofthe Cn or to use an assigned value of0.25. In 

### the 1979 final rule, DOE stated that setting the assigned value for Cn at 0.25 gives manufac'turers incentive to test units with improved cycling performance; while at the same time, not severely penalizing manufacturers that elects to

use the assigned value. When DOE prescribed test procedures for heatpumps 

### in 1919, the assigned value for the degradation coefficient for heating was alBo set at0.25. This value

was selected because little information

wasknown concerning the heating degradation coefficienfand it

### was pnerallybelieved that the assigned values for cooling andheating

. degradation coefficient should be the l8Dle.



### Since 1919, DOE basbecome aware of information indicating thatmanyheat pumps are rated using the assigned value for the degradation coefficient because the assigned value typically

was lower (i. e. better) than the tested value. Using the assigned value instead ofthe actual value results in an unfair advantage in HSPF. when the assigned value is lower than the actual value. Purdue reported that the actual value averaged about 0.24. See 

### "Analysis of Heat Pump Test Data andIndustry's Response", HL81-37, Purdue University, February 1982. This implies that about one-halfofall heatpumps could obtain

an unfair advantage in HSPF by using the assigned value of0.25. DOE proposes to correct this problem by changing the assigned value for 

### Co for heating to 0.35. Setting the assigned value for CD at 0.35 would give manufacturers incentive to develop units with improved cycling performance. while not providing an unfair advantage to manufacturers that elect to use the assigned value. This philosophy is constant with the rationale used in the 1979 final rule. See 

### 3.1.1 ofAppendix M1 oftoday's rule.

c. Part-LoadFactors



### The DOE test procedures specify that SEER and HSPF shall be determined based on several variables, one of which is the part-load factor. The partload factor is an expression ofthe degradation ofa central air conditioner operating at various heating or cooling loads. The DOE test procedures assume that the degradation coefficient is linear. about a single cyclic test point. In reality, the degradation is non-linear and a series ofcyclic tests at various load conditions should be conducted. However. in order to reduce testing burden. the DOE test procedure specifies the cyclic tests at one load condition and assumes linearity for other loadings.

Recent studies have shown that the part-load factor can be expressed more accurately as an exponential function of the cooling or heating load factor. See 

### "Field Performance ofThree Residential Heat Pumps in the Cooling Mode". NBSIR 85-3107. March 1985 and "Field-

### Federal Register 

## I Vol. 51, No. 194 

## I Tuesday, October 

### 7, 1986 

## I Proposed Rules 

### 35739

Measured Cycling.**Fro~ting.** 

### and Defrosting Losses for a HighEfficiency Air-Source HeatPump", ASHRAE Transactions 1985, Volume 91, Part2- 

### DOE has reviewed these studiesto determine that the part-loadfactor can be expressedmore accuratelyby an exponential equation consisting of

### the cooling orheating loadfactor and the degradation determined by a single cyclic test in each mode (i.e. beating and cooling). This method involves no additional testing and is based on results from the already prescribed cycling tests. Since the exponential approach requires no additional testing and should potentially result inmore accurate ratings, DOE is today proposing that the part-load factors be determined by the exponentialmethod. 

### See 

### t 4.1.1 and4.2.1 ofAppendix Ml of today's notice.


### d. RatingProcedurefor Untested Combinations of Split-System Central AirConditioners

The December 1979 final rule stated that laboratory testing ofevery combination ofa split-system central air conditioner (i.e.• a separate condensing unit and evaporator coil combination) would unduly burden test procedures

users. Coil manufacturers stressed the impossibility oflaboratory testing all combinations that they offer for sale. Condensing unit manufacturers favored

an alternative to laboratory testing as long as it resulted in equal accuracy for their combinations. Consequently. in the December 1979 

### final rule. the Department allowed the use ofcomputer simulation or engineering analysis to predict the energy performance of untested combinations provided that, at

a minimum, laboratory testing was done

on the combination representing the largest sales volume, and the simulation technique demonstrated an acceptable level ofrepeatable accuracy. 

### See § 430.23(m)(5).



### Since 1979, 

### test procedures users have reported a high degree ofvariability resulting from the allowance ofusing simulation techniques. For example,

some utilities with rebate programs for the purchase ofhigh efficiency central air conditioners have reported receiving significantly different ratings for the

same condenser-evaporator-coil combination.

In 

### response to these issues. DOE directed NBS to evaluate various simulation techniques to determine the level of accuracy and repeatability. Concurrent with the NBS research, ARI contracted with ETL Testing Laboratories. Inc. (ETL), a private testing laboratory, to conduct a testing program which would compare results ofsimulation techniques in use with actual testresults. Theseefforts indicated that although some simulation techniques appear to have reasonable accuracy.otbertechniques demonstrated significant variability of results. In the interest ofimproving this situation. NBS. working in conjunction with ARI. 

### ETL. condensing unit 

### manufacturers, coil manufacturers and consulting engineers, has developed a standardizedrating method for untested combinationsofsplit-systems. DOE published the standardized rating method as a Notice ofInquiry (NOI) on March 15, 1985, to receive comments and data concerning the accuracy and workability ofthe method. 50 FR 13042. April 2. 1985. DOE and NBS have reviewed the 24 comments received regarding the standardized rating method. See 

### "Rating Procedurefor

.Mixed Air Source Unitary Air Conditioners and Heat Pumps Operating in the Cooling Mode". NBSIR 86-3301, February 1986.

The standardized rating procedure for untested combinations that was published in the NOI was developed by NBS. The NOI procedure required knowledge ofthe following factors: (1) Capacity of the matched system; (2) indoor fan power of the mixed and matched systems; (3) coil capacity ofthe mixed and matched coils: (4) the type of expansion device on the mixed and matched systems; and the physical geometry of the expansion device on the mixed and matched systems. With these data the user could calculate the energy performance of an untested central air conditioner using the NOr rating procedure. Below is a discussion ofthe
comments that DOE received on the NO! rating procedure.

1. Comments Supporting the Standardized Rating Method

DOE received five comments supporting using the standardized rating method for all untested combinations of central air conditioners. Georgia Power Company commented that a standardized rating method is superior
to allowing multiple procedures and would simplify the rating process. (Georgia Power Company, No.1. at 1.)1 Texas Utilities Electric Company commented that even though laboratory testing is the best approach for rating central air conditioners, they recommended using a standardized rating method for all untested

1 Comments on tRe NOl were gillen docket numbers in which the citations provide the name of the orgsoizatioo. tbe docket number assigned to tbe
comment. and the page in which the comment is found in the commenter's submittal. 

### combinations ofcentral air conditioners. (Texas Utilities Electric Company. No. 12, at4.) Tennessee Valley Authority (TV

### A) commented that the standardized rating method should be adopted since it 

### appears to conservativelyestimate energy efficiency ratings without much risk ofoverstating systemperformance and since the input parameters are readily available. (TVA. No. 20. at 1.) Magna Flow Industries. 

### Inc. (Magna Flow) supported using a singlerating method which would allow real and meaningful comparisons in the marketplace. (Magna Flow. No. 21, at 2.) Airmax. Inc. (Airmax) agreed with using

a standardized rating method that would eliminate the disparity between ratings done by different coil manufacturers on the same condensing unit and similar coils. (Airmax. No. 22. at 1.)

2. Comments Opposing a Standardized Rating Method

Seven commenters opposed adoption ofa standardized rating method. ETL commented that actual laboratory testing should be the only acceptable approach for rating central air conditioners. (ETL. No.8, at 1.). Six coil manufacturers. Red T Coil ( a division of the Coleman Co., Inc.), Superior Coils, Inc, International Environmental Corporation. First Company. Magic Aire Division ofUnited Electric Co

.. and Texas Coil Company, all opposed using

a standardized rating method because it 

### would result in lower ratings and would require proprietary information. (Red T Coil, No. 10, 

### at 1; 

### Superior Coils, Inc., No. 13, at 1; International Environmental Corporation, No. 14, at 2; First Company. No. 16, 

### at 2-5; 

### Magic Aire, No. 17, 

### at 1; 

### and Texas Coil Company. No. 19. 

### at 1.)



### The NOI stated that the standardized rating method could result in lower (conservative) ratings. According to research by NBS and others, the ratings from today's proposed standardized rating method. which includes some improvements in preciSion discussed below. appear to be closer to the ratings determined by laboratory testing and typically exhibit less scatter than ratings from the rating procedures NBS examined. Consequently, DOE believes that using the standardized rating method would result in more accurate ratings than other rating methods and would not necessarily result in lower (conservative) ratings.

The six coil manufacturers cited above also commented that the standardized rating method uses proprietary information from condensing unit manufacturers and that this information is not readily available. One objective that NBS had in developing

### 35740 

### Federal Register / Vol. 51. 

### No. 194 

### /Tuesday. October 7. 1986 / 

### Proposed Rules

the standardized rating method was that it

### did notrequire proprietarydata. l.fowever. in its research, NBS determined that to achieve an acceptable level ofaccuracy in the ratings. certain types ofinformation are required and that this information typically is not reported a8 accurately as the information required for the standardizedrating method. Consequently. NBS 

### discovered. attimes. that the standardizedrating method could result in unacceptablehigh variations in ratings unless certain precautions were taken to ensure that the input information was precise. Therefore. NBS 

### recommended that the power ofthe indoor fan. the refrigerant flow rate through the refrigerant expansion device, and the coil capacity for both the matched system and the mixed system should be determined precisely.

.

In the interest ofreducing testing burden and to assist manufacturers in obtaining this information, DOE has directed NBS to develop a. computer program for accurately determining coil capacities and to develop a test method for measuring the refrigerant flow rate through a refrigerant expansion device. DOE intends to incorporate the coil capacity computer program and the refrigerant flow rate test method into the 'est procedures once NBS completes Jevelopment ofthese procedures. During the interim period before they

are available. manufacturers can use industry-wide. currently acceptable

means for determining coil capacities and refrigerant flow rates (i.e.• coil capacity catalog data and physically measuring expansion devices for determining refrigerant flow rates).
3. Voluntary Certification and Enforcement Programs

Seven commenters recommended that central air conditioners subject to the ARI certification program for unitary air-conditioning and air-source heat pump equipment should not be required to use the standardized rating procedure for rating untested combinations. In the ARI certification program. participating manufacturers must file certification data with ARIon all models subject to the program. Participating manufacturers include ARI members and is open to non-ARI members. The data are carefully reviewed by ARI and laboratory tests are conducted by an independent testing laboratory to verify the data when the data is questionable. In addition. ARI conducts random testing ofall models and participating "anufacturers may request additional**~sting** 

### ofcompetitor's models ifthe participating manufacturer questions the competitor's ratings. Consequently. the commenters contend that rating certified byARI cannot exhibit the high degree of variability mentionedpreviously in today's notice. These commenters further contend that manufacturers subject to the ARI certification program shouldnot 

### be required to use the standardizedrating method since the rating methods used in the ARI program could. potentially. bemore accurate than the standardizedrating method. These commenters also recommended that the standardizedrating procedure should 

### be required for untested systems not covered bythe ARI certification program. (Bard. No.2. at 1; ARI. No.3. at 2; Aspen. No.4. at 1; Rheem. No.5. at 1; Trane. No.7. at 2; Borg-Warner. No. 15. at 2; and Snyder General. No. 18. page 1.)



### DOE agrees that ifa manufacturerhas

an alternative rating method which is

more accurate than the standardized rating method, the manufacturer should be allowed to use the alternative rating method. However. before a manufacturer can use the alternative method. he must obtain approval by DOE in accordance with 

### I 430.23(m)(5) ofthe proposal. The Department believes that all alternative rating methods must be reviewed in order to maintain integrity in the ratings. Consequently. manufacturers who have previously received approval by DOE to

use an alternative method must resubmit that method to DOE before it can continue to use the alternative method for rating central air conditioners. The process for obtaining approval is more structured than the current process. primarily to maintain more control over manufacturers who elect to use alternative methods and to better ensure that the alternative methods result in fair ratings.

One critical part ofthe approval process is that the manufacturer must submit sufficient information in its request in order for DOE to be able to make a determination concerning whether the alternative method is more accurate than the standardized method. At a minimum. this would require that the rating procedure is traceable to actual test data. a complete documentation ofthe alternative method. including the computer code when a computer model is used; ratings for two complete lines ofcoil families for two different condensing units; and complete test data, product information and related information to allow DOE to verify the ratings submitted by the manufacturer.

The rating information submitted by the manufacturer for the mixed system would include ratings determined by testing. bythe standardizedrating method and by the alternative rating method. This would allow DOE to compare ratings determined by the

...

ting methods to ratings from actual testiDg inorderto determine whether the alternative method is more accurate than the standardized method. Another provision is thatratings arerequired for two complete lines ofcoil families for two different condensing units and that the capacities ofthe matched system using the two condensing units must vary by atleast a factor oftwo. DOE is proposing these provisions which require ratings for different coil lines and condensing units to determine whether the alternative method can be widely used for rating all types. sizes and combinations ofcondensing units and coils. DOE believes that the information requested must be provided in order to make a valid determination.

Furthermore. DOE is proposing that manufacturers who elect to use an alternative rating method must have their ratings verified by either an independent testing program or an independent state registered professional engineer. In 

### addition. today's proposal would require that whenever rated values do not agree within two percent ofthe values as determined by testing. the actual test data shall be used for energy efficiency representation.
4. Rating Procedure Requires Accurate Information

Aspen commented that even with a near-perfect standardized rating method. results could be meaningless if the input information is inaccurate or if restrictions specified in the DOE procedures are ignored. (Aspen. No.4. at 2.) 

### DOE is aware that the rating method could result in unacceptably high variations in ratings ifno precautions

were taken to ensure that the input information was precise. For this reason. today's notice includes additional requirements concerning determining the power ofthe indoor fan. the refrigerant flow rate through the refrigerant flow device. and the coil capacity for both the matched and mixed systems. Regarding the comment by Aspen that restrictions in the DOE test procedures were ignored. DOE proposes changes to the rating method to better ensure that these restrictions

are followed.
5. Credit for TXV Valves

Aspen and Texas Utilities Electric Company both recommended that the standardized rating method allow a

### Federal Register 

## I Vol. 51. No. 194 

## I Tuesday. Octooor 

### 7, 1986 

## I Proposed Rules 

## 35741

credit for mixed systems equipped with thermal expansion valves (TXV) when the matched system does not have a TXV. (Aspen. No.4. Appendix A. at 1 andTexas Utilities Electric Company. No. 12 

### at 2.) 

### Both companies presented test data in which the SEER was 9.0

### for

a matched system and 9.45 mixed system. 

### In the example. the matched system did not have a TXV while the**mix~d** 

### system did have a TXV. 

### By using the rating method published in the NOI. the SEER was calculated to be 8.17. 

### However, the calculated 

### SEER was9.22 

### with a credit for the TXV. Since the rating was closer to the tested value when a credit was allowed (the difference between therated value and the tested value was 2.4 percent when a credit is allowed and 7.2 percent without

a credit). both Aspen and Texas Utilities Electric Company recommended a credit for TXV·s.

According to NBS. a TXV generally is

a superior expansion device that should increase the SEER. However. not aU systems would expect the same increase in efficiency by using TXV·s. For example. based on research conducted by NBS. the improvement in SEER is expected to be 2.5 percent for TXV's with "bleeding" and 5 percent for TXV's with "no bleeding" TXV's, where bleeding refers to the characteristic ofa TXV to relieve pressure differences by leaking refrigerant across the device during the off-period. TXV's with no bleeding which prevent off·cycle migration of the refrigerant. generally

are superior to TXV's with bleeding. which allow off-cycle refrigerant migration.

In consideration ofthe comments by Aspen and Texas Utilities Electric Company and ofthe research conducted by NBS. DOE is proposing to include a thermostat expansion value factor in 

### the standardized rating method for mixed systems with TXV·s. This factor is based on the 2.5 percent lmprovement for TXV's with bJeerling and 5percent improvement for non-bleeding TXV"s recommended by 

## r'..'Bs. See 

### Appendix M1 to Subpart 430 section 4.1.6.2.

6. Adjustment for Fan Power

Aspen recommended that tke ratio of the power of the mixed system to the matched system at 82 'F {PX!PM)82 be 

### adjusted for differences in indoor fan power between the matched and mixed systems. (Aspen. No.4. Appendix B. at 1-2.) 

### This ratio is one ofthe factors used in determining the SEER for the mixed systems. This adjustment would take into account the effect different units would have on system efficiency.

NBS has reviewed the approach recommended by Aspen for adjusting (Px/P,.ln to determine that the rating method would result in more accurate ratings when differences 

### in indoorfan powerare properly considered. 

### In Its review. 

### NBS developed a slightly qifferentmethod for correctingfor

. indoorfan powerthat the Aspen method. T-oday's proposal adjusts

## (P,,/ p••



### lnfor differences in indoorfan power and is basedon the NBS recommended method. 

### See Appendix

### Ml to Subpart 430. 

### eactions 4.1.6.3 

### 'find 4.1.6.4,

7. 

### AdjustmentforDegradation Coefficient

Fourcommenters, Rheem. Addison. Trane and Lennox, stated that the standardized rating method does not properly account for changes in cycling losses by adjusting the degradation coefficient. CD' (Rheem. No.5, at 2; 

### Addison, No.6. at 1; Trane. No.7, at 2; 

### and Lennox, No.9 at 2..) 

### In 

### investigating whether adjusting for changes in the degradation coefficient between the matched and the mixed systems would improve the accuracy 

### ofratings. NBS determined that there is a relatively large allowed experimental tolerance in determining the value ofthe degradation coefficient. This was due to allowed experimental tolerances in test procedure set-up. testing equipment and test procedures. NBS also determined that the change in the degradation coefficient between the matched and mixed systems would generally be much less than the allowed experimental tolerance from testing. This implies that most ofthe difference in the degradation coefficients reported by laboratory testing between the matched and mixed systems would be attributed to the testing itself and would not properly reflect for differences in cycling losses. Consequently. DOE has not changed the rating method to account for differences in degradation coefficients.
8. Expansion Device Scaling Factor

Rheem noted that in the equation for the ratio ofthe capacities of the mixed system to the matched system at 82 OF (QX/QM}8'2. 

### the exponent for the expansion device scaling factor was 0.44 for capillary tubes end TXV's and was 0.35 for orifices. Rheem commented that the exponent should be the same and not dependent on the type ofexpansion device used. (Rheem. No.5. at 3.) This ratio is one of the factors used in determining the SEER for the mixed system. The expansion device scaling factor {F.} 

### is the ratio ofthe refrigerant

mass flow rates through the mixed and matched expansion devices at the same operating conditions.

NBS reviewed Rheem's comment and agreed that the exponent should be 8 

### constant and recommended 0.35 as the value to be used. Today's notice

. specifies 0.35 

### as the exponent for the

expanaion device Icaling factor in 

### the equationfor determining (Qx/Q..)u.



### In addition. Rheem commented that a lowerlimit 

### of0.8 

### and 

### an upperlimit of 1.2 

### should beplaced on the expansion device scalingfactor because as the difference between the refrigerant mass Dow rates through the mixed and matched expansion devices increases. the accuracy decreases. (Rheem. No. 

### 50 at3.)



### Inthe NOI, a lowerlimit of0.85 was placed on the expansion device scaling factor. At that time. no upperlimit was made because it was not considered to be necessary. In 

### consideration of Rheem's comment. NBS reviewed data for the expansion device scaling factor
to determine that the method can be 

### used ifthe factor is between 0.85 and 1.35.



### Today'snotice specifies that the standardizedrating method can be used ifthe expansion device scaling factor is between 0.85 and 1.35. DOE believes that these values represent the extreme oftypical scaling factors and the Department does not have data on units with scaling factors outside this range to determine ifthe standardized rating method yield accurate results. For mixed systems with expansion device scaling factor outside this range. the standardized rating meeting can not be used for rating purposes. For these systems, ratings can only be 

### detennined by testing.

9. Accountability

Rheem commented that manufacturers participating in the ARI certification program are held accountable for their ratings. implying that manufacturers who will use the standardized rating method are not held accountable for their ratings. [Rheem. No.5, at 3.) Manufacturers. whether using the DOE
test procedures. computer simulation or engineering analysis. have always been held accountable for their ratings. Section 430.23[m)(3) ofthe DOE test procedures states that whenever

measures ofenergy consumption detennined by computer simulation or by engineering analysis do not agree with measures of energy consumption detennined by actual testing. the values determined by actual testing shall be used. To continue to ensure that manufacturers using the rating method

are held accountable for their ratings. DOE has proposed a similarprovision in today's notice. 

### See § 

### 430.Z3(m){3).

### 35742 

### Federal Register 

# I Vol. 51, No. 194 

# I Tuesday. October 7. 1986 

# I Proposed Rules

10. eoil Capacity

Addilon commented that the ratina method**~liel** 

### ondeterminina coil capacitiel from coil manufacturers catalogl,Addilonfurther commented thatthele catlilOSS cannotalwaysbe used for determinina the capacitiesfor both thematched andmixed system coils because thematched ormixed coil desip canbeofa unique desigri which is notincluded inthe catalop. (Addison. No. 8, 

### at %.) 

### DOE agreel with Addison that there are certainlimitations with usina coil catalogues for determinina

. coil capacity: however. DOEbelieves thele catalogues canbe used in the majority ofcalel.AI mentioned above. DOE had directed NBS to develop a computer program to alsist manufacturers in determinina coil capacitiel. Once a coil capacity

. computerprogram has been developed it will be incorporated into the test procedures.

11. Double Orifice FlowDevices

Lennox commented that the standardized ratina method does not address a system using two orifice flow devices in series and that this device is used extensively. (Lennox. No.9. at 1.) DOE is aware that the rating method does not address systems that use combinations ofexpansion devices. which is one reason why DOE directed NBS to develop a refrigerant flow test method that would address combinations ofexpansion flow devices. including the double orifice flow device mentioned by Lennox. Until such test method is incorporated into the standardized rating method. these designs can be rated by actual tests or by a DOE approved rating method.

12. Coil Circuitry

Lennox commented that coil capacity

can be determined by computer simulation only ifthe simulation method properly addresses coil circuitry. (Lennox No.9. at 1.) The coil simulation program. which NBS is presently developing. will address coil circuitry to result in more accurate ratings for mixed systems. Until such a test method is incorporated into the standardized rating method. these designs can be rated by actual tests or by a DOE approved rating method.

13. Validation ofthe Rating Procedures

Texas Utilities Electric Company recommended that the rating method should be validated against actual laboratory test results. (Texas Utilities Electric Company. No. 12. at 4.) 

### The rating method was initially validated by NBS for 22 different systems whenDOE published the NOI.

.



### In response to the NOI. DOEreceived additional comparisons betweenresults from theproposedratinamethod and actual 

### testiqfrom Rheem. Trane and Borg.Warner. manufacturers ofmatched

.systems. (Rbeem. No. 5, at 5-8;

### Trane. No•." at 3: andBorg.Warner, No. 15, at 3.) Based on thiJ information, the proposedratina method was revised for indoorfan power, a creditforTXV'a. 

### and different limits for the coil capacity

. ratio. NBS also had a consultina eqineercompare the revised

. procedures against actual testresults as
an independent check ofthe ratina procedure. DOE believes that today's standardized ratina method will produce ratinas that are comparable with results from testing andno further validation is necessary. 14. Expand Ratina Procedures for Heating

TVA recommended that DOE should develop a similar standardized rating method for the heating function ofheat pumps. (TVA, No. 20. Page 1.) DOE has directed NBS to develop a rating method for the heating function ofheat pumps and is evaluating the procedures other organizations. e.g. ARI. are developing. Until such a test method is incorporated into the standardized rating method. these designs can be rated by actual tests orby a DOE approved rating method.

e. 

### Ground Water-Source Heat Pumps andEarth-CoupledHeat Pumps

Today. DOE is proposing test procedures for two types ofwatersource heat pumps. ground water-source heat pumps and earth-coupled heat pumps. A ground water-source heat pump utilizes a refrigerant-to-water heat exchanger(s) in which ground water is circulated to and from the heat exchanger(s) in an open loop. An 

### earthcoupled heat pump utilizes a refrigerantto-water heat exchanger(s) in which water to and from the heat exchanger(s) is circulated through the ground in a closed loop. DOE is proposing test procedures only for these designs of water-source heat pumps because they typically are used in residential applications. whereas. all other types of water-source heat pumps are generally used solely for commercial applications.

In 

### 1979. DOE proposed test procedures for water-source heat pumps based upon recommended procedures from NBS. However. test procedures for water-source heat pumps were not included in the 1979 final rule because commenters stated that the proposed procedures for water-source heat pumps werenotconsistentwith the ones for air-source heatpumpa.These

. commenters contended that the inconsistencies couldgive erroneous

. costinformation. and encourage sales of

oneproduct overanother. 

### In view of these comments, DOE directed NBS to develop andrecommend appropriate
testprocedures for water-source heat pumps.

Today's notice specifies the same test procedures forbothground water-

sourcebeatpumps and earth-coupled heatpump. and are based onARI Standard 325-8S 

### and onresearch

.conducted by NBS. See 

### "Laboratory Tests ofa Residential Unitary WaterSource Heat Pump", NBSIR 81-2287. November 1982 and "Method ofTesting. Rating and Estimating the Seasonal Performance ofGround -WaterSource Heat Pumps", NBSIR 81-2434. November 1982. The NBS Method is based on four steady-state tests: a high temperature cooling test (70 eF). a low temperature cooling test (SO eF). a high temperature heating test (70 eF) and a low temperature heating test (SO en

DOE. is todayproposing that SEER andHSPF are calculated using a seasonal part-load factor of0.90 for SEER and 0.85 for HSPF. ifthe water-

source heat pump does not require any supplemental resistance heat. For units that require supplemental resistance heat DOE is proposing a bin method of calculating SEER and HSPF similar to the existing heat pump calculation procedure. 

## f. Split-Type Ductless S}'stems

A split-type ductless system is a relatively new product design that has recently been marketed in the United States that is not covered by the current test procedure. A split-type ductless system is a central air conditioner with

a remote condenser or remote condenSing unit and one ormore ductless indoor fan-coil units. One feature that distinguishes these systems from other types ofcentral air conditioners and heat pumps is that the split-type ductless system with multiple indoor units can operate in a multiple

zone control mode in which each indoor unit is a separate zone and that each indoor unit will operate only upon demand.

DOE believes that the special design characteristics of split-type ductless systems will result in materially inaccurate and unrepresentative data for these systems ifthey are tested by the existing DOE test procedures. The DOE test procedures specify that the unit must be connected to ductwork whereas split-type ductless systems are

### Federal Register 

# I Vol. 51, 

### No. 194 

# I Tuesday, October 7, 1986 

# I Proposed Rules 35743

installed without ductwork. Specifying a testing condition for ductwork for splittype ductless systems would result in an abnormally high pressure drop across the indoor unit, resulting in unwarranted reductions in both capacity and

. efficiency. Consequently, DOE directed NBS to develop a test procedurefor split-type ductless systems.

NBS developed a test procedure for split-type ductless systems based, whereverpossible, onANSII 

### ASHRAE Standard 116-83 

### and 

### ARI Standard

### 2101 24G-84. 

### See "Procedure for Testing, Rating and Estimating the Seasonal Performance ofMultiple-Indoor-Coil Residential Air Conditioners and Heat Pump", NBS letter report. AprilS. 1985. 

### DOE has reviewed the NBS testing approach andbelieves that it 

### can be used for testing split-type ductless systems. Today's notice specifies that for split-type ductless systems with multiple indoor units, the outdoor unit would be tested separately for each combination ofindoor units. DOE believes that this provision is necessary to provide complete information to

consumers because as the split-type ductless system operates with fewer indoor units it 

### tends to become less efficient. DOE believes that this information is important, especially if

consumers operate the split-type ductless system with several indoor units turned off.

Section 8.2.2.lb ofA;."IJSI/ASHRAE Standard 116-1983 specifies that the indoor supply duct shall be blocked during the defrost cycles in the Frost Accumulation test. DOE considers this to be an unrealistic operating condition for split-type ductless systems because these systems do not operate in this

manner. Consequently. today's notice specifies that the indoor supply would not be blocked during the test.

Today's notice specifies that during cyclic testing ofmultiple indoor units. a single control circuit would be substituted for multiple thermostats in order to maintain a uniform cycling rate. Today's notic.e also specifies that the thermostats'for the indoor units would be shunted during the steady-state tests. These testing provisions. which are in addition to the test procedures in ANSI/ ASHRAE Standard 116-1983 and the ARI Standard 210/240-84. are considered necessary to complete the test procedures for split-type ductless systems.


### 8. Variable-SpeedHeatPumps

In 1981. OHA granted an exception to York for its variable-speed heat pump. 

### FederalEnergy Guidelines. 7 DOE section 81.209. In 1983. OHA extended the exception to Borg-Warner. formerly York. 

### FederalEnergy Guidelines, 10 DOE section 81,306. These two exceptions specified 

### an alternative test procedure for testing and rating variable-speed heat pumps. "



### In 1988, 

### CarrierpetitionedDOE for. test procedure waiverfor 

### its variablespeed heatpump. February 14, 1988. 51 FR 5587. 

### Carrierpetition specified 

### an alternative test procedure different from the York approach.



### ARI Standard**210/~** 

### also specifies an alternative test procedure" " for evaluating variable-speed heat "_" pumps. 

### See ARI Standard**210/~,** 

### Appendix S, Rating Equipment with Variable-Speed Compressors.

Today's notice w(>uld extend coverage ofthe test procedures for variable-speed heat pumps to all firms manufacturing variable-speed central air conditioners and heat pumps. As such. the final rule would tenninate the exception relief granted by OHA to both York and BorgWarner for theirmodels ofvariable- " speed heat pumps and the test procedure waivergranted to Carrierfor Us models ofvariable-speed heat pumps.

DOE has reviewed the three methods for determining ratings for variablespeed heat pumps developed by BorgWarner. ARI and Carrier. All three methods are similar in determining SEER and all require a steady-state cooling test at an intennediate compressor speed to accurately reflect the performance ofthe unit while it 

### is operating between the minimum and maximum compressor speeds. Consequently. DOE believes that all three methods should result in similarly accurate and comparable ratings for SEER.

The ARI method does not include a steady-state heating test at an intermediate compressor speed; the Borg-Warner and Carrier methods do include such a test. For this reason. DOE believes that both the Borg-Warner and Carrier methods could. potentially. result in more accurate ratings for HSPF than the ARI method. Consequently. the ARI method has not been adopted for today's proposal.

There is one key difference between the Borg-Warner and Carrier methods. The Borg-Warner method uses an optional separate steady-state healing test at the intermediate compressor speed for each design heating requirement to accurately describe the performance ofthe heat pump operating between the minimum and maximum compressor speeds. The Carrier method requires a single steady-state heating

., test at one intermediate compressor speed and then determines analytically the performance of the heat pump operatingbetween the minimum and maximum compressor speeds for each design heating requirement. DOE believes that both methods should result in Similarly accurate and comparable ratings for HSPF. Since the Carrier method is less burdensome byrequiring only one additional test. DOEhas based the method for determining HSPF for variable-speedheatpumps on the Carrier method. "
h. 

### Transition Period

Today'.notice would replace, in its entirety. the existill8 test method for central air conditioners. 

### In order to reduce the burden ofretesting existing models, today's notice would provide for testing by eithermethod during a twoyear transition period follOWing the publication date ofthe final rule. Specifically. the existing test method remains as Appendix 

### M while the proposed test method is Appendix Ml. After the two-year transition period. only Appendix M1 would be allowed. The present test method (Appendix M) 

### would no longer be allowed and would be deleted, from the DOE test procedures.

In addition. ratings for untested combinations of split-system central air conditioners would be determined in accordance with new § 

### 430.23(m)(5}. There would be no transition period for rating untested combinations of splitsystem units.

New basic models ofcentral air conditioners and heat pumps manufactured after the effective date of the final rule shall be tested only by the test procedures specified in Appendix Ml. Appendix M 

### cannot be used for testing new basic models. DOE believes that this transition period will minimize any retesting burden.

III. Comment Procedures



### a. Written Comments

Interested persons are invited to participate in the rulemaking by submitting data. views. or arguments with respect to the proposed amendments set forth in this notice to the address indicated at the beginning of the notice.

Comments should be identified on the outside ofthe envelope and on documents submitted to DOE with the designation "Central Air Conditioner Test Procedures. Docket No. CAS-RM79-102". Seven (7) 

### copies are requested
to be submitted. All comments received by the date specified at the beginning of this notice and all otherrelevant information will be considered by DOE before final action is taken on the

### 35744 

### Federal Register 

## I Vol. 51. 

### No. 194 

## I Tuesday. October 7. 1986 

## I Proposed Rules

proposedregulation.Pursuant to

### the

rovisionsof10CFR 1004.11. anyperson JbmittiDl information which he

### or .he oeUeves to be confidential and exempt by lawfrom publicdiac10sure .hould submit ODeoompletecopy 

### of

### the documentand6 copies. 

### ifpossible.from which theinformation believed to

### be confidentialhas been deleted. DOE

### will make its own determination withregard
to the confidential status 

### ofthe information and treat it accordill8lo its determination.

Factors ofinterest toDOE when evaluatill8requests to treat as confidential information thathas been submitted include: {I) A description of the item; (2J an indication as to whether and why such items ofinformation have been treated by the submittingparty as confidential. and whether and why such items are customarily treated as confidential within the industry; (3) whether the information is generally known or available from other sources; (4) whetherthe information has previously been made available to others without obligation concerning its confidentiality; (5) an explanation ofthe competitive injury to the submitting person which would result from public disclosure; (6) an indication as to when such information might lose its

1nfidential character due to the Issage oftime; and (7) whether .Jisc\osure ofthe information would be in the public interest.


### b. PublicHearing

1. 

### Proceduresfor SubmittingRequests to Speak

The time and place ofthe public hearing are indicated at the beginning of this notice. DOE invites any person who has an interest in today's proposed rule.

or who is a representative ofa group or class ofpersons that has an interest in the proposed amendments. to make a request for an opportunity to make an oral presentation. Such requests should be directed to the address indicated at the beginning ofthis notice and must be received by the time specified at the beginning of this notice. Requests may be hand delivered to such address between the hours of9:00 a.m. and 4:00 p.m

.. Monday through Friday. Requests should be labeled "Central Air ConditionerTest Procedures. Docket No. CAS-RM-79-102" both on the document and on the envelope.

The person making 

### the request should briefly describe the interest concerned and.. ifappropriate. statewhy he or she

'c; a properrepresentative ofthe group class ofpersollB thathave such an .terest, and give a telephone number where he or she may be contacted. 

### Each person

### to be

### heard is

### requested to submitleven(7) copies

### of

### Ju. or

### her
statement

### to 

### the address and 

### by the date Biven at 

### the beciDnill8

### ofthisnotice. 

### In the event any perIOn

# wiliams to testify 

### CBJUlOt meel 

### this requirement. alternative aJTanpments 

### cait bemade 

### with the Office 

### ofHearina

### andDockets in advance 

### of

### the hearingby ao

. indicatinsin 

### the letterrequesting to make an oralpresentation. 

### 2. ConductoJ Hearing

DOEreserves the right to select the persons to 

### be heardat this hearing. to schedule the respective presentations. and to establish the procedures governing theconduct 

### ofthe hearing. EachpresentationshaD 

### belimited to 20 minutes.

A DOE official will

### be designated to preside at the hearing.Thehearing will
not be a judicial or an evidentiary·type hearing. but

## win be conducted in accordance with 5 U.S.C. 553 and section 336 

### ofthe Act. At the conclusion ofall initial oral statements. eachperson who has made anoral statementwill be given the opportunity to make a rebuttal
statement The rebuttal statements will be given in 

### the orderin which the official statements were made and will be subjectto time limitations.

Any interested person who wishes to ask a question at the hearing may submit the question. in writing. to the presiding officer to be asked ofany person making a statement at the hearing. The presiding officer will determine whether the question is relevant and whether time limitations permit it to be presented for answer.

A transcript ofthe hearing will be made and the entire record of the hearing. including the transcript. will be retained by DOE and made available for inspection at the DOE Freedom of Information Reading Room. Room 1E152. Forrestal building. 1000 Independence Avenue. SW.• Washington. DC, between the hours of 8:30 a.m. and 4:00p.m

.. Monday through Friday. Forinformation concerning the availability ofrecords at the Freedom of Infor!Dation Reading Room. call (202) 252-5969. 

### In addition. any person may purchase a copy ofthe transcript from the reporter.

IV. Environmental Review

Pursuant to section 7{c)(2) ofthe Federal Energy Administration Act of 1974. a copy ofthis notice has been submitted to theAdministratorofthe Environmental Protection Agency for his
comments concerning the impact of 

### thil proposal on the 

### quality ofthe environment 

### Since 

### teatprocedures onderthe enellY conservationprogramfor consume!'products 

### will be used only to standardize

### the measurement ofenergy usage. and

### will not affect the quality of distributiChl 

### ofenergy usap. prescribing
test procedures

## win notresult in any environmental impacts. DOE. therefore has determined that prescribing test proceduresunder the 

### enel1Y conservationprogram for consumer products clearlyis not a majorFederal action significantly affecting the quality ofthe human environment within the meaning

### ofthe NationalEnvironment Policy Act of 1969. Consequently. neither an Environmental Impact Statement nor an Environmental Assessment isrequired for theproposed rule.

V. Review Under Executive Order 12291

Theproposed rule has beenreviewed in accordance with Executive Order 12291 which directs that all regulations achieve their intended goalI without imposing unnecessaryburdens on the economy. on individuals. onpublic or private organizations. or on State and local governments. The Executive Order also requires that regulatory impact analyses be prepared for "major rules". The Executive Order defines "major rule" as any regulation that is likely to result in: (1) An annual effect on the economy of$100 million or more; (2) a major increase in costs orprices for

consumers. individual industries. Federal. State. or local government agencies. or geographic regions; or (3) significant adverse effects on competition. employment. investment. productivity. innovation. or on the ability of the United States-based enterprises 

### to compete with foreignbased enterprises in domestic orexport markets.

The proposedrole would amend already·existing test procedures for central air conditioners and heat pumps. DOEhas determined that any burden imposed OD any person. industry. or government entity by the amendment of
extent procedures. based in part on commercial standards. is not sufficient
to being the proposed rules within the definition of "majorrule".

VI. Regulatory FleXlDility Act

The Regulatory Flexibility Act. Pub. L. 96-345 (5 U.S.C. 601-612). requires that

an agency prepare an initial regulatory flexibility analyses to be published at the time the proposed rule is published. This requirement (which appears in section 6(3) does not apply if the agency "certifies that the rule will not. 

### if promulgated have a significant 

# , I

11

### ~ 

# . , I.Federal 

### Register 

## I Vol. 51. No. 194 

## I Tuesday. October 7. 1986 

## I Proposed Rules 

## 35745

economic impact on a substantial

.**·~ber** ofsmall entities."The proposed affects manufacturers ofcentral air .lditioners and heat pumps. As previously discussed. the proposed changes would not have significant economicimpacts. but rather would simply improve the test procedures. Therefore. DOE certifies that the proposedrule. 

### ifpromulgated. would not have a "significant economic impact on
a substantial number ofsmall entities."

VII. Technical Support Documents

The following is a list ofthe technical support documents cited in today's proposed rule. These documents are listed in order ofappearance in the notice.

1. ANSI/ASHRAE Standard 116-81, "Methods ofTesting for Rating Unitary Air-Conditioning and Heat Pump Equipment

....

2. ARI Standard 210/240-84. "Standard for Unitary Air-Conditioning and Air-Source Heat Pump Equipment".

3. ANSI/ARI Standard 325-85,

. "Standard for Ground Water-Source Heat Pumps".

4. "Seasonal Performance ofAirConditioners-Experimental Analysis of the DOE Test Procedures Set Up Measurement Errors for Unitary AirConditioners and Heat Pumps", HL 82- T, Purdue University. May 1982.

5. "Seasonal Performance Characteristics ofAir-ConditionersAnalvsis of the DOE Test Procedures", HL 8:1-11. Purdue University. 1981.

6. "Trends ofResidential AirConditioning Cyclic Tests". ASHRAE Transactions 1982. Volume 88. Part 2.

7. "Analysis ofHeat Pump Data and Industry's Response", HL 81-37, Purdue University, February 1982.

8. "Field Performance ofThree Residential Heat Pumps in the Cooling Mode", NBSIR 85-3107. National Bureau of Standards. March 1985.

9. "Field-Measured Cycling. Frosting. and Defrosting Losses for a High Efficiency Air-Source Heat Pump". ASHRAE Transactions 1985, Volume 91. Part 2.

10. "Rating Procedure for Mixed Air Source Unitary Air Conditioners and Heat Pumps Operating in the Cooling Mode", NBSIR 86-3301. National Bureau of Standards. February 1986.

11. "Laboratory Tests ofa Residential Unitary Water-Source Heat Pump", NBSIR 81-2287, National Bureau of Standards. November 1982.

12. "Method ofTesting. Rating and Estimating the Seasonal Performance of Ground-Water Source Heat Pumps, NBSIR 81-2434, National Bureau of Standards. November 1982. 13. "Procedure for Testing, Rating and Estimating and SeasonalPerformance 

### of Multiple-Indoor-Coil Residential Air Conditioners and Heat Pumps". NBS letterrepoI:l. National Bureau of Standards.April 8. 1985.

In considerationofthe foregoing, 

### it is proposed to amend Part 430 ofChapter

. 

# nofTitle 10. Code ofFederal Regulations. as set forth below.

List 

### ofSubjects in

### .10 

## eFR Part430

Administrativepractice and procedure. Energy conservation, Household appliances.

Issued in Washington. DC, September 16, 1986. John R. Berg. Principal, DeputyAssistantSecretary. Conservation andRenewableEnergy.

PART 43D-ENERGY CONSERVATION PROGRAM FOR CONSUMER PRODUCTS

1. ·The authority citation for Part430 continues to read as follows:

Authority: Energy Policy and Conservation Act. Title III. Part B. 8S amended by National Energy Conservation Policy Act. Title IV. Part 2, (42 U.S.C.**6291~).**

1. Section 430.2 is amended by removing the definitions of "Air-source heat pump". "Cooling only unit", "Heat pump". and "Water-source heat pump" and by revising the definition of "Central air conditioner" to read as follows:

§ 430.2 Definitions.

"Central air conditioner" means an appliance which consists of one or more factory-made assemblies that normally includes an indoor conditioning coil(s). compressor(s) and outdoor coil(s) to provide either air cooling for coolingonly units or air heating and optionally. air cooling. for heat pumps; which may also provide air-circulating. air-cleaning. dehumidifying or humidifying; which is rated below 65.000 Btu per hour and is
not contained within the same cabinet

as a furnace whose rated capacity is above 225.000 Btu per hour; which is powered by single phase electric current; which is not equipped with a desuperheater/water heater device; and which includes the following products:

(a) "Air-source heat pump" means a central air conditioner which utilizes a refrigerant-to-outdoor-air heat exchanger and which provides air heating and optionally. air cooling.

(b) "Cooling-only unit" means a central air conditioner which consists of

an outdoor air-cooled condensing unit and an indoor evaporator coil and which provides air cooling. (c) "Earth-coupled heatpump" means 

### a central airconditioner which utilizes a refrigerant-to-waterheat exchanger(s) in which the waterfrom the heat exchanger(s) is circulated through the ground in a closed loop and which· provides airheating and optionally. air cooling;

(d) "Ground**water-sour~e** heat pump"

means a central airconditioner which utilizes a refrigerant-to-water heat exchanger(s) inwhich the waterfrom the heat exchanger(s) is circulated through the ground in an open loop and which provides airheating and optionally. aircooling.

2. Section430.22 is amended by revising paragraph (m) to read as follows:

§ 430.22 Teat procedure, for measures of 

### energy consumption. * * 

### * 

## • •

(m) 

### Centralairconditioners. (1) The estimated annual operating cost for cooling-only units and air-source heat pumps shall be one ofthe follOWing:

(i) For cooling-only units or the cooling portion ofthe estimated annual operating cost for air-source heat pumps which provide both heating and cooling. the product of: (A) The quotient ofthe cooling capacity. its But's per hour. determined from the steady-state wetcoil test (Test A) measured at the highest compressor speed. as described in section 3.1 ofAppendix M or section 3.1 ofAppendix M1 to this subpart. divided by the seasonal energy efficiency ratio. in Btu's per watt-hour. determined from section 5.1 of Appendix M or section 4.1 of Appendix M1 to this subpart; (B) the representative average

use cycle for cooling of 1.000 hours per year; (C) a conversion factor of0.001 kilowatts per watt; and (D) the representative average unit cost of electricity in dollars per kilowatt-hour

as provided pursuant to section 323(b)(2) ofthe Act. the resulting product then being rounded off to the nearest dollar per year;

(ii) For air-source heat pumps which provide only heating or the heating portion of the estimated annual operating cost for air-source heat pumps which provide both heating and cooling. the product of: (A) The quotient of the standardized design heating requirement. in Btu's per hour. nearest to the capacity measured in the high temperature test. determined in sections 5.2 and 6.2.6 of Appendix M or section 3.1 of Appendix M1 to this subpart. divided by the heating seasonal performance factor. in Btu's per watthour. calculated for heating region IV corresponding to the above mentioned

### 35746 

### Federal Register 

## I Vol. 51. No. 194 

## J Tuesday. October 7, 1986 

# I Proposed Rules

standardized design heating requirement determined from section 

### 5.2 ofAppendix M orsection4.2 ofAppendixM1 to this subpart (B) therepresentative averase 'se cycle for heating of%,080hours per ear; {C) 

### the adjustment factorof0.77 which serves to adjust 

### the calcualted design heatingrequirement and heating load hours to the actual load experienced

### by a heating system; (O) a conversion factor of0.001 kilowatts 

### per watt; and (E) the representative average unit cost ofelectricity in dollars per kilowatt-hour as 

### provided pursuant to section 323{b)(2) of

### the Act. the resulting product then beingrounded offto the
nearest dollar per year; or

{iii) For air-source heat pumps which provide both heating and cooling, the estimated annual operating cost is the

sum ofthe quantity determined in paragraph (m)(l)(i) ofthis section added
to the quantity determined in paragraph (m)(l)(ii) ofthis section.

(2) The estimated annual operating
cost for earth-coupled heat pumps and ground water-source heat pumps shall be one ofthe following:

(i) The cooling portion ofthe estimated annual operating cost, is determined from section 4.7 ofAppendix M1 ofthis subpart for the maximum design cooling requirement at region IV,

as determined from section 4.5.2 of Appendix M1 to this subpart, being rounded off to the nearest dollar per ·'ear;

(til The heating portion of the stimated annual operating cost is determined from section 4.7 of Appendix Ml of this subpart for the maximum design heating requirement at region IV,

as determined from section 4.5.2 of Appendix Ml to this subpart, being rounded offto the nearest dollar per year: Of

(iii) For earth-coupled heat pumps or ground water-source heat pumps which provide both heating and cooling. the

sum of the quantity determined in paragraph {m}(2)(i) ofthis section added
to the quantity determined in paragraph (m)(2J(ii) of this section.

(3) The estimated regional annual operating cosl for cooling-only units and for air-source heal pumps shall be one of the following:

{il For cooling-only units or the coolil18 portion ofthe estimated regional annual operating cost for air-source heat pumps which provide both healing and cooling. the product of: {A) The quotient of the cooling capacity, in Btu's perhour, determined from the steady-state wetcoil test (Test A) measured at the highest compressor speed. as described in section 3.1 of Appendix M or section 3.1 ofAppendix M1 to 

### this subpart. -1ivided by the seasonal energy efficiency ratio. 

### in Btu'sper watt-hour. determined from section 5.1 ofAppendix M or section 4.1 ofAppendixMl to this subpart; (B) the eatimatednumberof regional cooling 

### load boW'S peryear determined from section 6.1.3 of Appendix 

### M or 

### Figure 1 ofAppendix 

### M2
to 

### this subpart; {C) a conversion factor of0.001 kilowatt.per watt and (D) the representative average unit cost of electricity 

### in dollars perkilowatt-hour

as provided pursuant toeection 323(b)(2J ofthe Act. the resulting product then beingrounded off

### to the nearest dollar peryear;

(ii) For air-sourceheatpumps which provide only beating orthe beating portion ofthe estimated regional annual operating cost for air-source heat pumps which provide bothheating and cooling, the product of: tA} The quotient ofthe standardized design heating requirement, in Btu's perhour. nearest to the capacity measured in the high temperature test (Test A). determined in sections 5.2 and 6.2.6 ofAppendix M or section 3.2 ofAppendix Ml to this subpart, divided by the heating seasonal performance factor. 

### in Btu's per watthour. calculatedfor the appropriate region ofinterest and corresponding to the above mentioned standardized design heating requirement determined from section 5.2 ofAppendix M or section 4.2 ofAppendix Ml to this subpart; fBJ the estimated number of regional heating load hours per year determined from section 6.2.5 of Appendix M or Figure 2 of Appendix M1
to this subpart: (C) the adjustment factor of0.77 which serves to adjust the calculated design heating requirement and heating load hours to the actual load experienced by a heating system; (D) a conversion factor of0.001 kilowatts per watt; and (El the representative average unit cost of electricity in dollars per kilowatt-hour

as provided pursuant to section 323(bJ(2l ofthe Act. the resulting product then being rounded offto the the nearest dollar per year; or

(iil) For air-source heat pumps which provide both heatiIl8 and cooling. the estimated regional annual operating cost is the sum ofthe quantity determined in paragraph {m)(3)(il of this section added
to the quantity determined in paragraph (m)(3)(iiJ ofthis section.

(4) The estimated regional annual operatil18 cost for earth-coupled heat pumps and ground water-source heat pumps shall 

### be one ofthe following:

(il The cooling portion ofthe estimated annual operating cost is

.determined from section 4.7 ofAppendix M1 of this subpart for the appropriate standardized design cooling requirement
at the region ofinterest. as determined from section 4.5.2 ofAppendix Ml to this subpart,

# hems rounded offto the
nearest dollar

### per

### year;

(ii) Theheatingportion ofthe estimated annual operating cost is determined from section4.7 ofAppendix Ml to this subpart forthe appropriate standardized designheatiD8 requirement
at the region ofinterest. beingrounded offto the nearest dollarperyear; or

[iii) Forearth-coupledbeatpumps or ground water-sourceheatpumps which provideboth heating and cooling, the

sum ofthe quantity determined in paragraph (m)(4)(i) 

### ofthis section added
to the quantity determined inparagraph (m)(4Jlii) ofthis section.

. (5) The measurers) ofefficiency for cooling-only units and air-source heat pumps shall be oneormore ofthe following:

(i) The seasonal energy efficiency ratio for cooling-only units and airsource heat pumps which provide cooling shall be the seasonal energy efficiency ratio. in Btu's per watt-hour. determined according to section 5.1 of Appendix M or section 4.1 ofAppendix M1 to this subpart. rounded offto the nearest 0.05.

(ii) The heating seasonal performance factors for air-source heat pumps shall be the heating seasonal performance factors. in Btu's per watt-hour. determined according to section 5.2 of Appendix M or section 4.2 ofAppendix Ml to this subpart for each applicabJe standardized design heating requirement within each climatic region, rounded off
to the nearest 0_05.

(iii) The annual performance factofs for air-source heat pumps which provide heatil18 and cooling. shall be the annual performance factors. in Btu's per watthour,determined according to section 5.3 of Appendix M or section 4.3 of Appendix Ml to this subpart for each standardized design heating requirement within each climatic region. rounded off
to the nearest 0.05.

(6) The measurers) of efficiency for earth-coupled heat pumps and ground
water-source heat pumps shall be one or
more of the following:

(i) The seasonal energy**efficieDc~'** ratio for earth-coupled heat pumps and ground water-source heat pumps which provide cooling shall be the seasonal energy efficiency ratio. in Btu's per watthour, determined according to section 4.4 of Appendix Ml to this subpart. rounded off to the nearest 0.05.

(ii) The heating seasonal performance factors for earth-coupled beat pumps and ground water-source heat pumps which provide healing shall be the heating seasonal performance factors, in Btu's per watt-hours. determined

### Federal 

### Register 

## I Vol. 51. 

### No. 194 

## I Tuesday. October 7. 1986 

## I Proposed Rules 

## 35747

according to section 4.5 

### ofAppendix M1 to this subpart for each applicable standardized design heating requirement within each climatic region. rounded off
to the nearest 0.05.

(iii) 

### The annual performance factors for earth-coupled heat pumps and ground water-source heat pumps which provide heating and cooling. shaJJ be the annual performance factors. in Btu's per watt-hour. determined according to section 4.6 

### ofAppendiX M1 to this subpart for each standardized design heating requirement within each climatic region. rounded offto the nearest 0.05.

(7) 

### Otheruseful measures ofenergy consumption for central air conditioners shall be those measures ofenergy consumption which the Secretary of Energy determines are likely to assist

consumers in making purchasing decisions and which are derived from the application ofAppendices M and M1 to this subpart. '

(8) For a transition period of24 months from the effective date ofthis amendment, all measures ofenergy consumption shall be determined either by the uniform test method for measuring energy consumption of central air conditioners, as set forth in Appendix M of this subpart or by the amended test method for measuring energy consumption ofcentral air conditioners. as set forth in Appendix Ml of this subpart. After the tran.,ition period. all measures ofenergy consumption shall be determined only bv the amended test method as set forth in Appendix Ml ofthis subpart; the uniform test method, as set forth in Appendix M ofthis subpart shall no longer be used.

3, Section 430.Z3 is amended by revising paragraph (m) to read as follows:

§ 430.23 Units to be tested. 

## • • (m)(l) For central air conditioners, each condensing unit shall have a condenser-evaporator coil combination selected and a sample of sufficient size tested in accordance with applicable provisions ofthis subpart such that-

(i) Any represented value ofestimated annual operating cost. energy consumption or other measure ofenergy consumption of the condenserevaporator coil combination for which

consumers would favor lower values shall be no less than the higher of (A) the mean ofthe sample or (Bl the upper 90 

### percent confidence limit ofthe true

mean divided by 1.05, and

(ii) Any represented value ofenergy efficiency or other measure ofenergy consumption ofthe condenserevaporator coil combination for which consume1'8 would favor higher values sha)) be no greater than the lowerof(AJ the mean ofthe sample or (B) 

### the lower 90 

### percent confidence limit ofthe true

mean divided by0.95.

(2) 

### The condenser-evaporator coil combination selected for tests pUl'Buant to paragraph (m)(1) ofthis section shall be that combination manufactured by the condensing unit manufacturerlikely to have the largest volume ofretail sales. Components ofsimilardesign may be substituted without requiring additional testing ifthe represented

measures ofenergy consumption continue to satisfy the applicable sampling provisions ofparagraphs (m)(l) (i) and (iiJ. For every other condenserevaporator coil combination 'manufactured by the same manufacturer

orin part by a component manufacturer using that same condensing unit, either-

.

(iJ A sample ofsufficient size. comprised ofproduction units or representing production units, shall be tested to insure that the requirements of paragraphs (m)(l) (i) and (ii) 

### are met for such other condenser-evaporator coil combinations; or

(ii) The representative values ofthe

measures ofenergy consumption shall be based on the standardized rating method in section 4.1.6 ofAppendix M1 to this subpart; or

(iii) The representative values ofthe

measures ofenergy consumption shall be based by an alternative rating method that has been approved by DOE in accordance with the provisions of paragraphs (m) (4) and (5) of this section.

(3) Whenever the representative "'alues ofthe measures of energy consumption. as determined by the provisions ofparagraphs (m)(Z) (ii) 

### and (iii) ofthis subpart, do not agree within Z percent ofthe representative values of the measures ofenergy consumption as determined by actual testing, the representative values determined by actual testing shall be used to comply with section 3Z3(c) the Act, or to comply with rules prescribed under section 3Z4 ofthe Act.

(4) The basis ofthe alternative rating method referred to in paragraph (m)(Z)(iii) ofthis section shall be a representation ofthe mechanical vapor compression refrigeration cycle. The 'major components in the refrigeration cycle shall be modeled as "fits" to manufacturer performance data or by graphic or tabular performance data. Heat transfer characteristics ofcoils may be modeled as a function offace

area. number ofrows, fins per inch, refrigerant circuitry. air flow rate and entering airenthalpy. Additional performance-related characteristics to 

### be considered may include type of expansion device. refrigerant flow rate through the expansion device. power of the indoor fan and degradation coefficient.

(5) Manufacturers who elect to use an alternative rating method for determining measures ofenergy consumption under paragraphs (m)(2)(iii) and (4) ofthis sectionmust submit a request to DOE for revising the alternative rating method to the Assistant Secretary ofConservation and Renewable Energy. 1000 Independence Avenue SW.• Washington. DC 20585. and receive approval to use alternative method by the Assistant Secretary before the alternative method can be used for rating central air conditioners.

(6) Each request to DOE for reviewing

an alternative rating method shall include:

(i) 

### The name, address and telephone number of the official representing the manufacturer.

(ii) 

### Complete documentation of the alternative rating procedure. including the computer code when a computer model is used.

(iii) 

### Ratings for two complete lines of coil families for two different condensing units. The tested capacities for the matched svstems for the two condensing units shall differ by a factor of two. Rating information for the mixed systems shall include the ratings from testing. from the standardized rating method and from the alternative rating method.

(iv) Complete test data. product information, and related information to allow DOE to verify the rating information submitted by the manufacturer.

(7) 

### Manufacturers who elect to use an alternative rating method for determining measures ofenergy consumption under paragraphs (m) (Z)(iii) and (4) of this section must either subject a sample oftheir units to
, independent testing on a regular basis (e.g., voluntary certification program) or have the representations reviewed and certified by an independent State registered professional engineer who is
not an employee ofthe manufacturer. The registered professional engineer is to certify that the results ofthe alternative rating procedure accurately represent the energy consumption of the unit(s) and are more representative of the unit's performance than the standard rating procedure in § 

### 430.23(m)(Z)(ii). The manufacturer is to keep the registered professional engineer's

### 35748 

### Federal Register 

## I Vol. 51, No. 194 

## I Tuesday, October 7, 1986 

## I Proposed Rules

c:ertifications on file for review by DOE for as long as said combination made

IIlilable for sale by the manufacturer. (8) Fornew basic models ofcentral air conditioners and heat pumps manufactured after the effective date of the final rule, the models shall be tested according to the provisions inAppendix Ml ofthis subpart.

4. Subpart BofPart430 is amended by adding Appendix Ml 8S 

### follows: Appendix Ml To Subpart B-AmendeelTest Method for Measuring the Energy Consumption ofCentral Air Conditioners

1.0Definitions. Definitions shall include the definitions specified in Section 3.0ofARI Standard 210!24(}-64. Section 3.0 ofANSI/ ARI Standard**32~5,** Section 3.0 ofANSII ASHRAE Standard 116-1983 and the follOWing additional definitions.

1.1 "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 power used in

one year.

1.2 "ANSI" means the American National Standards Institute.

1.3 "ANSI/ARI Standard**32~5"** means the test standard published in 1985 jOintly by ANSI and ARI and titled "Standard for Ground Water-Source Heat Pumps".

1.4 "ANSI!ASHRAE Standard 37-1978"

means the test standard published in 1978 jointly by ANSI and ASHRAE and titled "Methods ofTesting for Rating Unitary AirConditioning and Heat Pump Equipment".

1.5 "ANSI/ASHRAE Standard 116-1983"

eans the test standard published in 1983 Jointly by ANSI and ASHRAE and titled "Methods ofTesting for Seasonal Efficiency of Unitary Air-Conditioners and Heat Pumps".

1.6 "ARI" means the Air-Conditioning and Refrigeration Institute.

1.i "ARI Standard 210/24G-84" means the test standard published in 1984 by ARI and titled "Standard for Unitary Air-Conditioning and Air-Source Heat Pump Equipment".

1.8 "ASHRAE" means the American Society ofHeating. Refrigerating and AirConditioning Engineers, Inc.

1.9 "Continuously recorded" means a method ofrecording measurements in intervals no greater than 5 seconds.

1.10 "Cyclic test" means a test where the indoor and outdoor conditions are held constant. but the unit is manually turned "on" and "off' for specific time periods to simulate part-load operation.

1.11 "Demand-defrost control system"

means a system which is designed to perform the defrost function on the outdoor coil ofthe heat pump only when a predetermined degradation of performance is measured.

1.12 "Design cooling requirement (OCR)"

means the amount ofcooling required to maintain a given indoor temperature at a particular outdoor design temperature.

1.13 "Design heating requirement [DHR)"

means the amount ofheating required to maintain a given indoor temperature at a 'larticular outdoor design temperature.

1.14 "Dry-coil test" means a test conducted "t a wet-bulb temperature and a dry-bulb temperature such that moisture will not condense on the evaporatorcoil ofthe unit

1.15 "Latent cooling" means the total amount ofcooling in Btu's necessary to

. remove watervapor from the airpassing over the indoor coil by condensation during a period oftime.

1.16 "Matched system" means a testeel combinationofa split-system central air conditioner.

1.17 "Mixed system"· means an untested coinbination ofa split-system central air conditioner in which the ratings are determined by4.1.6 ofthis appendix.

1.18 "Part-load factor (PLF)" means the ratio ofthe cyclic enel'8Y efficiency ratio to the steady-state enel'8Y efficiency ratio at identical ambient conditions.

1.19 "Sensible cooling" means the total amount ofcooling in Btu's performed by a unit over a period oftime, excluding latent cooling.

1.20 "Single package unit" means a central air conditioner in which the compressor. condenser, evaporator and fan are enclosed in a single assembly.

1.21 "Split system" means a central air conditioner with a remote condenser or remote condensing unit.

1.22 "Split-type ductless system" means a central air conditioner with a remote condenser or remote condensing unit and one
or more ductless indoor fan-coil units.

1.23 "Steady-state test" means a test in which all the indoor and outdoor conditions

are held constant and the unit is in a nonchanging operating mode.

1.24 "Temperature bin" means a 5'F ,increment over a dry-bulb temperature range of 65 OF through 104 OF for the cooling cycle and -25 OF through 64 OF for the heating cycle.

1.25 'Time-temperature defrost control system" means a system which automatically provides the defrost function at a predetermined time interval whenever the outdoor temperature drops below a level where frosting will occur.

1.26 'Test condition tolerance" means the maximum permissible variation of the average of the test observations from the standard or desired test conditions as prOVided in Table III-A or ANSI/ASHRAE Standard 116-1983 for air-source units and in Table 5 of this Appendix for water-source units.

1.27 "Test operating tolerance" means the maximum permissible difference between the maximum and the minimum instrument observation during a test as provided in Tables III-B and Ill-C ofANSI/ASHRAE Standard 116-1983 for air-source units and in Table 5 ofthis Appendix for water-source units.

1.28 "Wet-coil test" means a test conducted at a wet-bulb temperature and a dry-bulb temperature such that moisture will condense

on the test unit evaporator coil.

2.0 Testing conditions. 2.1 Testing conditionsfor cooling-only units andair-source heatpumps. For coolingonly units and air-source heat pumps, testing conditions shall be as specified in section 5.0 ofARI Standard 210/24(}-64, with the inclusion ofthe following conditions.

2.1.1 Split-type ductless systems. The follOWing paragraph is in addition to the requirements specified in section 5.1.3.5 pf ARt 210/240-84:

For split-type ductless systems. all standard rating tests shall be performed with

a minimum length of25 feet of interconnecting tubing between each indoor fan-coil unit and the common outdoorunit.

2.1.2Additionaltesting conditionsforsplittypeductless systems. For split-type ductless systems. 

### a single control circuit shall be lubstituteel for anymultiple thermostats in order to maintain 

### a uniform cycling rate during test D and the high temperature heating cyclic test. During the steady-slate
tests. all thermostats shall be shunted resulting in all indoorfan-coil units being in operation.

2.1.3Additionaltesting conditionsfor cooling-only units andair-source heatpumps with variable-speedcompressors. For cooling-only units and air-source heat pumps with variable-speed compressors. the air flow
rate at fan speeds less than the maximum fan speed shall be determined by using the fan laws for a fixed resistance system. The air flow rate is then given by the ratio ofthe actual fan speed to the maximum fan speed multiplied by the air flow rate at the maximum fan speed. Minimum static pressure requirements only apply when the fan is running at the maximum speed.

2.2 Testing conditionsfor earth-coupled heatpumps andground woter-source heat
pumps. For earth-coupled heat pumps and ground water-source heat pumps. testing conditions shall be as specified in section 5.0 ofANSI/ARI Standard 32fr1985.

3.0 Testprocedures. 3.1 Testproceduresfor cooling-only units andair-source heatpumps. For cooling-only units and air-source heat pumps, test procedures shall be as specified in section 5.0 of ARl Standard 210/241l-B4 and in section 8.0 ANSI/ASHRAE Standard 116-1983, with the inclusion ofthe following conditions.

3.1.1 Cyclic test. The following paragraphs

are in place of section 5.1.3.1 ofARl Standard 210/241l-B4.

5.1.3.1 Cyclic tests. For units other than variable-speed units, heating and cooling cyclic tests shall be conducted by cycling the compressor(s) 6 minutes "on" and 24 minutes "off'. The capacity and all electrical energy shall be measured for the integration time (8,] of six (6) minutes. All off-cycle electrical energy shall be measured for the total integration time (Bevel of 30 minutes. Offcycle electrical energy does not include the fan power.

For variable-speed units, heating and cooling cyclic tests shall be conducted by cycling the compressor 12 minutes "on" and 48 minutes "off'. The capacity and all electrical energy shall be measured for the integration time (B), of 12 minutes. All offcycle electrical energy shall be measured for the total integration time (8

....) of 60 minutes. Off-cycle electrical energy does not include the fan power.

In lieu ofconducting C and D tests, and assigned value of0.25 shall be used for the degradation coefficient for cooling, CD' In lieu of conducting the high temperature heating cyclic test, and assigned value of0.35 shall be used for the degradation coefficient for

### Federal Register 

## I Vol. 51, No. 194 

## I Tuesday, October 7, 1986 

## I Proposed Rples 35749

heatins.

### C.Forunita with the two compressorspeeds. two compressorsor cylinderunJoadins. ifthe .ssigned desradation coefficient is Uled for one coolins mode. itmust be used for both cooling modes. Ifthe assigned degradation coefficient is 

### uaed for one heatins mode. it must beusedfor both heatinsmode•.

3.1.2Ail'4Durc:. uni,. with variable-speed compressors. 'I1Ie followins provisions are iii place ofthe provisions in Appendix BofARI Standard2t0/24O-M for the intermediate coolins steady-state te.t.

Forair-source units with variable-apeed comprellors. an intermediate cooling .teady- .tatete.t .hall be conducted in which the unit .hallbe operated at a constanl, intermediate compressor .peed (K= V 

### J in which the dry-bulb and wet-bulb temperatures ofthe air entering the indoor coil and the outdoorcoil selected for the intermediate coolins steady-.tate test are at the temperatures .pecified for the intermediate cooling steady-state test in Table B1 ofARI Standard 210/240-84. The tolerances for the dry-bulb and wet-bulb temperature. ofthe airentering the indoor and outdoor coils .hall be the test operating tolerance and test condition tolerance specified in Table III-A ofANSI/ASHRAE Standard 116-1983. The intermediate

. compressor speed shall be within 10 percent 

### ofthe average ofthe maximum and minimum compressor .peeds. '.

For air-source unita with variable-speed compre ••

o

.... the frost accumulation test shall beconducted in which the unit shall be operated at a con.tant. Intermediate compressor speed (K-V.). 'I1Ie intermediate compressor speed shall bewithin 10percent 

### ofthe aver.,.ofthe maximum aDd minimum compressor .peeds.

3.1.3 Split-t}'PB ductlesssystems. The followins parasfaph i.in addition to the requirements specified in section B.Z.2.1.b of ANSI/ASHRAE Standardtt&-1983.

.

For split-type ductle.s systems which tum the indoor fan offdurins defrost. the indoor

•upply duct shall not beblocked.

3.2 Testproceduresfor eorth-coupledheat pumps andgroundwater-Bource heatpumps. For earth-coupled heat pumps andsround water-.ource heatpumps. test procedures shall be as specified in section 5.0 ofANSI/ ARI Standard 325-85. section 8.0 ofANSI/ ASHRAE Standard 37-78 and section 8.0 of ANSI!ASHRAE Standard 11&-1983.

4.0 Calculations. Calculations shall be as specified in 10 ofANSI/ASHRAE Standard 11&-1983. subject to the follOWing additional provisions. The equation for determining the flow rate ofstandard air (Qs). as determined in 6.7.3 ofANSI/ASHRAE Standard 11&-1983. is replaced by the following equation: 

### Q.

... Q

..
0.075 V.

where: Q..=measured indoor airflow rate. nil/min o.o75-d8Dsity ofstandard air.lb/nll V.-.pecificvolume ofairat nozzle. nll/lb of air-watermixture
4.1 Seasonalenergyefficiencyratioforair-

.oureeunits. 'I1Ie sea.onalenergy efficiency ratio (SEER) thall be expre.sed in Btu per watt-hour • 4.1.1 Seasonalenergyefficiencyroliofor air-souree units with single-speed
compressors. For air-source units with Single- .peed compressors. SEER shall be defined as the cooling seasonal energy efficiency ratio (SEER) as specified in 10.1.2 ofANSI! ASHRAE Standard 11&-1983. with the followins added provisions. One. the number ofhours in the jUl temperature bin (n)) in the equations for the capacity (q(t,)) and for the
power input (E(1j)) is defined in Table 1 of this Appendix. Two. the part-load factor (PLF) in the equation for the power input (E(t))) is defined as:



### for 

### CLF ( 0.70

PLF 

# = (1

- CLF)(l

- PLF(0.70» 0.30

where: Er=exponential factor and is defined as: Er=1.9In 125 CD CLF=coolingload factor. as defined in 10.1.2 ofANSI/ASHRAE Standard 116-1983 PLF (0.70)

## =part-load factor at a cooling load factor of0.70. as determined above CD=degradation factor. as defined in 9.2.2 of ANSI/ASHRAE Standard 116-1983 or is assigned the value of0.25.
4.1.2 Seasonal energy efficiencyrotiofor air-source units with two-speedcompressors

ortwo compressors. For air-source units with two-speed compressors or two compressors. SEER shall be defined as the cooling seasonal energy efficiency ratio (SEER) as specified in 10.1.3 ofANSI/ASHRAE Standard 116-1983 in which the number ofhours in the j'" temperature bin (n)) in the equations for the cooling capacity (q(t,)) and for the power input (E(t))) is defined in Table 1 ofthis Appendix and in which the part-load factor (PLY) in the equation for the power input (E(t))) is defined in 4.1.1 ofthis Appendix.

4.1.3 Seosonal energy efficiencyrotiofor air-source units with triple-capacity compressors. [Reserved]

4.1.4 Seasonal energy efficiencyrotiofor air-source units with variable-speed
compressors. For air-source units with variable-speed compressor. SEER shall be defined as the seasonal energy efficiency 

# -

for 

### eLF") 0.70

ratio (SEER) as specified in 2.1 ofAppendix B ofARI Standard 210/240-84 in which the number ofhours in the jlh temperature bin (n)) in the equations for the capacity (q(t,)) and for the power input (E(t))) is defined in Table 1 ofthe appendix and in which the part-load factor (PLF) in the equation for the power input (E(t))) is defined in 4.1.1 ofthis appendix.

The SEER shall be determined by the method for two speed or two compressor units. as specified in ANSI/ASHRAE Standard 116-1983 and ARI Standard 210/ 240-84. and in accordance with the follOWing changes. The capacity for the unit modulating at the intermediate compressor speed (k=v)
at any**t~mperature** (t;) is determined by:

### 35750 Federal Register 

# I Vol. 51, No. 194 

# I Tuesday, October 7, 1986 

# I Proposed Rules



## k=v

.. • q '(87) + 

# Mq (tj-87)



# . Where: k=V q 

## (87)· the capacity of 

## the unit at 87 0

## p 

## determined by the intermediate coOling steady-state test


## Mq • slope of 

## the capacity curve for the intermediate compressor .speed (kav)

M 

# =

q



## + 

## N q 

# * 82 67


## 0'<=2(95)



## ss 95 

# * (1



## Ok=2(82)

ss 82

Oka 

## v(87)

ss Ok=l (87) ss N

q 

## = Ok=2(87) ss Ok=1(87) ss

Once the equation for**q~.'** It;) has been determined. the temperature where**q~='** (tJ)=BL(t,) can be found. This temperature is designated as (tve) and replaces 87 'F in the equations for Case II in Appendix B ofARt Standard 210/240-&1.

The electrical power input for the unit operating at the intermediate compressor speed (k=v) and the temperature [t,.) is determined by:



## where:

# E~:v(87) = the electrical power input of the unit at 87 0 

### F 

## determined by the intermediate cooling stea1y-state test



# = slope of the electrical power input curve for the intermediate compressor speed (k=v)**M~** 

# =

....

N,.. &:

.ti

Once Ek:;' (t•• ) has been determined. it 'eplaces E":: (87) in the equations for Case I in Appendix BofARI Standard 210/240-&1.

4.1.5 Seasonal energy efficiency ratiofor split-type ductless systems. For split-type ductless systems. SEER shall be defined as 

## EI<=1(82) ss 82

Ek=V(87)

ss

Ek=2(87)

ss 67



## 82

Ek=1(87)

SS



## Ek=1(87)

ss
specified in 4.1.1 ofthis appendix for each combination ofindoor coils to be used with a
common outdoor unit.

4.1.6 Seasonalenergy efficiencyratio and capacityfor untestedcombinations ofsplitsystem centralairconditioners. For untested combinations of split-system central air conditioners. the capacity at 95 OF (Q.) and the seasonal energy efficiency ratio (SEER.) are determined by the following equations:

BlWNG COOE

...50-01

....

### Federal Register 

# I Vol. 51, No. 194 

# I Tuesday, October 7,1986 

# I Proposed Rules

S££Rx •



## wbere:

# l~t

# -\":

+ 

# !:!5

# ~:t.aJ 

# · .p

. 

## ,.0.35 

# * Fa

- 3.25 

## !.l.a.&

.



## . c

...e . Om

# (~) - 0.8 

# * FO.14 

# * pb 

## + 

## 0.1 

# !L.x + 

## 0.1 Pm 82 c . e Pr,m 

# _ { :0.15 for

## Fe~ 1

a 

## for Fe<l

b • 

# { o for Fe?l

for Fe<l

. -0.2



## Fe • indoor coil scaling factor, as determined in 4.1.6.1 of this ,ppendix

F • expansion device scalin; factor, as determined in

e Table 6 of this**~ppendix FT~J**  

# = thermostatic**exp~nsion** 

## valve factor, as determined in Table 6 of**t~is ~ppenjix**  

## P

F • power input to the indoor fan of the matched system,

,m as determined in 4.1.6.3 of this Appendix

P

F • power input to the indoor fan of the mixed system, as

,x determined in 4.1.6.4 of this Appendix

Om • capacity at 95°F of the**mat~hed** 

## system, as reported in the currentARI Directory of Certified Unitary AirConditioners and Unitary Air-Source neat Pumps 

# /0)= ratio of the capacities of the mixed system**\~** 

## to the matched system at 82°F

m 82 

# l ? 

# )= ratio of the power of the mixed system to the**~** 

## matched system at 82°F

m 

# a2

• seasonal energy efficiency ratio of the matched

. system, as reported in the current ARI Directory of Certified Unitary Air-Conditioners and Unitary Air-Source Heat Pumps 35751

### 85752 

### Federal Register 

# I Vol. 51. No. 194 

# I Tuesday. October 1. 1986 

# I Proposed Rules

..

1.8.1 

### IndoorcoilMXJIi",

### /actor. The indoorcoillCAJins factor 

### (fJ determined bythe fonowiDl equation:

where: 

### Qc..**~** 

# --- CQc..

Q...-cooliDacapacity ofthe mixed coil at theairma

..

# now rate specifiedfor the matched .y.tem Q...-coolinacapacity ofthe matched coil at the indoor

..

irvolumetric

# now rate (CFM.) at which the matched .ystem capacity (Q.) was mea.ured. IfCFM. is
not known. it canbe determined by:

f25*Q. CFM.,-- 12.000

Capacities ofthe matched and mixed coils shall be determined by the same method and
at the followina conditions: Inlet air conditions of80 'Fdry bulb and 67 'Fwet bulb; 45 'Frefrigerant saturation temperature; and the same refrigerant superheat at the

- evaporator outlet. Ifcoil capacities are obtained by means ofa catalog or computer simulation. the same catalog or computer simulation shall be used for both coils. Coil material and geometry (e.g

.. inside tube diameter. tube staggering. fin spacing. fin thickness. fin shape, and number oftube depth rows) shall be accounted for by the method used. That is, the methodology used
must have these parameters as independent variables. This rating procedure cannot be used ifFe is smaller than 0.8. Ifthe ratio of 

### Q

•.•/Q

.... is greater than 1.3. then F. shall be defined as 1.3. Ifthe rating is calculated for a heat pump system able to operate in the heating mode. two additional conditions have
to be satisfied:

(1) The internal volume ofthe mixed indoor coil assembly shall be within 100-120percent ofthe internal volume ofthe matched coil assembly; or shall not exceed the volume of the matched coil assembly; or shall not exceed the volume ofthe largest coil certified with a given condensing unit by the condensing unit manufacturer. which everis largest.

.

(2) Condensing capacity ofthe mixed coil shall be within 100-120 percent ofcapacity of the matched coil; or shall not exceed the capacity ofthe largest certified coil. whichever is largest.

4.1.6.2 Expansion device scalingfactor. The expansion device scaling factor (F.) is the ratio ofrefrigerant mass flow rates through the mixed and matched expansion devices at the same operating conditions and c:iepends on the types ofmatched and mixed expansion devices used. Values for F. are --eported in Table 6 ofthis appendix. The

B

ting procedure shall not be used if: -The mixed Iystem has a combination of capillary tubel or orifices connected in serier. 

### -Thematc:hed ayllem

### hal a cOmbination ofcapillarytubes ororifices connectedin

. aeriea unleu the mixed syetem

### hal a 

### TXV;

-Thematched .yetem

### hala 

### TXV anclthe mixedlyetem

### hal eithera capillarytube or

an orifice. unleu the condeuaiDa unit

. manufacturers certifie. altoa ayaIem which a 

### TXV itreplaced by a capillarytube ororifice type expansion device. In .uch

### a canthis .yetemmaybe couidered asa matched lyetem and itaperformance data maybe 

### uaed for calculation ofperformance ofthe mixed ayatem:

-Theupaniion device ICAlina factor. F

.. II outside the ranae0.95-1.35 for sy.tems operatinainthe coolina mode only;

-The expan.ion device acalinafactor. 

### F

.. i.outside the ranp 1.00-1.25for system. operating in both thebeatinaand coolina mode.

ForCases

### I to 

### IV. 

### F. shall be determined below. where subscripts 1and; correspond to the numberofcapillary tubes or orificies connected in parallel in the mixed and matched expansion devices. respectively. 0 denotes the inner diameter. L denotes the length ofa capillary tube oran orifice in inches. Theinner diameter and length are to be measured to an accuracy of ±1.5%. Subscripts. and DI refer to the mixed and matched expansion devices. respectively.

Case I

For a matched system and a mixed system, both consisting ofcapillary tubes. Fe shall be defined as:

.

F. 

### =---

The flow factors "' •.1and "'m.; for capillary tubes in the mixed and matched systems are determined by theirgeometry and by the 1983 ASHRAE Handbook. Equipment Volume, Chapter 20. Figure 38.

Case II

For a matched syslem consilting of capillary tubes and a mixed system consisting oforifices, F. shall be defined as:

l: ..".;

F. = 109.6

...;

where:

72200 D' •.I
"'

••1 = ------"'-'---- [0.58+0.008 

### CL.

. 

### .I0•.i)]U

"'

• .j..,al defined above in CaleI
CasellI

For a matched system consisting oforifices and a mixed system consisting of capillary tubes. F. shall be defined as: 109.8 % •••1 

### F.

- %

....
where:

•

......definedabovein eanl

7Z2OO0·

.... 

# ....

# - ------;;;;.;...--- (0.58+0.008 (L..

../D •.

J)

..•


## ea.e1V

Fora matched aystem and a mixed .ystem.

. both conlistina oforifices.

### F. shallbe defined



# ..:

%

.... F •• -.-- %

..,•• ,

where:

..,

....=a. defined in Case II

•• ,,=a8 defined in CaseJU 4.1.6.3 Powerinputtothe indoor fan of the lIIatchedsystem.

Formatched systems equiped with indoor fans, the power input to the indoorfan (P'.m) shall bemeasured in accordance with ARI Standard 210/240-84 and at the same indoor air volumetric flow rate (CFMm) at which the capacity ofthe matched system (Q

..) was measured. IfCFMm is not known. it shall be defined al:

425Qm CFM,.,=-.

- 12,000

For matched systems not equipped with indoor fans. PFolI shall be defined as: Pr

.M =0.365 CFMm

4.1.6.4 Powerinput to the indoorfan of the mixedsystem.

For mixed systems equipped with indoor fans. the power input to the indoorfan (Pr .•) shall be measured in accordance with ARI Standard 210/240-84 and at the same indoor air volumetric flow rate (CFM.) at which the capacity of the mixed B}'stem (Q.) was measured. For mixed systems not equipped with indoor fans. Pr .•• hall be defined as: Pp••=O.365 CFM.

4.2 Heating seasonalperformancefactor for air-source units. The heating seasonal performance factor (HSPF) shall be expressed in Btu per watt-hour. Foreach of the six regions specified in Table 2 ofthis appendix. a separate HSPF shall be determined for the standardized maximum OHR, the standardized minimum OHR and for all other standardized OHR's (See Table 3 ofthis Appendix) between the maximum and minimum values.

For air-Iource units that are equipped with "demand defrost control systems", the value for HSPF. as determined above shall be multiplied by an enhancement factor. F

...,· to compensate for improved performance not measured in the Frost Accumulation Test.

The factor. File, depends on the number of defrost cycles in a 12-hour period (n) and should be calculated as follows:

### Federal Register 

## I Vol. 51, No. 194 

## I Tuesday, October 7, 1986 

## I Proposed Rules 35753

Where: 

### N-l 

### F.., _1+0.04_



# .,

0-721.)/t. or 8, whicheveriI.maller



## PLF

where: E,=exponential factor and is defined as:

1.25 Ep 

## = 1.91nCo

HLF=heating load factor. as defined in 10.1.2 ofANSI/ASHRAE Standard 116-1983 PLF(0.70)=part-load factor at a heating load factor of0.70. as determined above CD=degradation factor. as defined in 9.2.2 of Al'lSI/ASHRAE Standard 116-1983 or is assigned the value of0.35 4.2.2 Heating seasanalperformance factorfor air-source units with two-speed
compressors or two compressors. For airt=lensth ofthe defrost accumulation teat period in minutea 

### 4.2.1 Heating seasonalperformQI/CII factor

### forai1'4DUI'CB wiIB with BingJINpeed 

### compressors. For air-source unitt with .ingle- .peedcompressol'8, HSPF .hallbe defined u the heatins seasonal performance factor (HSPF) as .pecified inlD.2.2 ofANSI{ ASHRAE Standard**11~1983** multipliedby 8.413 Btu/watt-hour. with the followins addedprovisions. One. thenumber ofhours inthe

,... temperature bin (nJ in the equations for HSPF andfor the .upplementary

- resi.tance heat term (RH (tJ) is dermed in Table2 of

### this appendix: 

### Two. the part-load factor (PLF) in all the equations HSPF is defined 

### a.:



## (1

- HLi> (1

- PLi(0.70», for

## HLF~ 

## 0.70 

# 0:-30

source unit8 with two-speed compressors or two compressors. HSPF shall be defined as the heating seasonal performance factor (HSPF) as speCified in 10.2.3 ofANSI/ ASHRAE Standard**11~1983** multiplied by 3.413 Btu/watt-hourin which the number of hours in the j'b temperature bin (nJ) in the equations for HSPF and for the supplementary resistance heat term (RH (t))) is defined in Table 2 ofthis appendix and in which the part-load factor (PLF) in the equation for the power input (E (t;)) is defined in 4.1.2 of this appendix.

4.2.3 Heating seasonalperformance factorfor air-source units with triblecapacity compressors. [Reserved]

4.2.4 Heating seasonalperformance factorfor air-source units with variablespeedcompressors. For air-source units with variable-speed compressors. HSPF shall be defined a8 the heatins seasonal performance factor (HSPF) as specified in 2.2 ofAppendix BofARI Standard 210/240-84 multiplied by 3.413 Btu/hr in which the number ofhours in the jUl temperature bin (n)) in the equations for HSPF and for supplementary resistance heat term (RH (t))) is defined in Table 2 of this Appendix and in which the part-load factor (PLF) in the equation for the power input (E(t))) is defined in 4.2.1 of this appendix.

The HSPF shall be determined by the method for two speed or two compressor units. as specified in ANSI/ASHRAE Standard 116-1983 and ARI Standard 210/ 240-84. and in accordance with the following changes. The capacity for the unit modulating
at the intermediate compressor speed (k= V)
at any temperature (t;) is determined by:



## qK=V(tj) = 

## qk=v (35) 

## + Mq (tj

- 35)



## where: qK=v(35) 

## = the capacity of the unit at 35 0 

## F 

## determined at the intermediate compressor speed (k=v) in the frost accumulation test

Mq

N

## q 

## = slope of the capacity curve for the intermediate compressor speed (k=v)

k=l (62) k= 1 (47) Oss Oss

= 

# * ( 1 

## - N ) 62 47 

## q

k=2 (47) k=2 (17) 

## Q

ss

- Oss 

## + N

## q 47 17

Ok=v

ss (35) Ok=1 ss (35) 

# = Ok=2 5S 

## (35) Ok=1 ss (35)

### 35754 

### Federal Register 

## I Vol. 51, No. 194 

## I Tuesday, October 7. 

### 1986 

## I Proposed Rules

Once theequationfor qI'-(t,)

### halbeen "'etennined. the temperature where

- -"(tJ-81.(t,) can be found. 'I'hH .emperature i.designated as t\IB- A aeparate



## where:

....\(=1 .!:iss ME =

+ N£ 

### Iva shallbe determinedJoreachdeaip heatill8 requirement.

Theelectrical powerinput for theunit operatill8 atthe intennediate ComPlellOf apeed (k-v) and at the temperature (t\'8) is determined by:



## the electrical power input of the unit at 3SoF determined at the intermediate compressor speed (k=v) in the frost accumulation test : slqpe of the electrical power input curve for the intermediate compressor speed (k-v)

(62)
_ Ek=1 

## (47) 

## ss 

# * (1 - N

...) 

### 62



## - 47 .co



### ... k=2 

## (47)

_ Ek=2 

## (17) l:i 

## ss 55


## 47


# - 17

Ek=v

55 

### (35) 

### _ Ek=l
55 

### (35)



### = NE 

### Ek=2 55

The following section replaces Case II in section 2.2 ofARI 210/240-84. 

## (35) Ek= 1 55 

### (35)

Case II

When the compressor speed varies between the maximum speed (k=2) and minimum speed (k=1) such that k=v to satisfy the building load at temperature tj evaluate the following equations:

81LlING CODE 6450-01

....

### Federal R

.... 

### ter 

# I Vol. 51, No. 194 

# I Tuesday, October7, 1988 

# I Proposed Rules



## where:

where: kav 

## qss (tj , a 

## steady-state capacity delivered by 

## the unit at any speed between the minimum and maximum compressor spee4s at temperature tj

+ . kal Ek

- 

## v 

## Ess (t3 ' - ss (tVH)

t3

- 

# tva : 

# * (t·

- 

### tvH) 

### . 1



## the ele=trical power input required by the unit at temperature t· and at a variable compressor speed**betw~en** 

## the minimum and maximum compressor speeds

It=v Ess (tVH) 

# = the electrical power input required by the' unit at temperature 

# tvn and at the intermediate compressor speed (k=v), as determined above

the electrical power input required by the unit at temperature t3 and at the minimum compressor speed
t) 

# = temperature at which

when tj

# « tVH k=l gss (tj) = BL(tj)

+



# -----

k=2 

## where: Ess (t4> - the ele6trical power input required by the unit at temperature t4 and at the maximum compressor speed

1t=2 

## t4

- temperature at which gss (tj>· BL(tj'

BIWNG CODE**~1~**

### 35756 Federal Register 

## I Vol. 51, No. 194 

## I Tuesday, October 7, 1986 

## I Proposed Rules

For air-source units with variable-speed compressors that are equipped with "demand defrost control systems", the value for HSPF.

1S determined above. shall 

### be multiplied by 

## In enhancement factor of 1.04 to compensate for improved performance not measured in the Frost Accumulation Test.

4.2.5 Heating seasonalperformance foetorforsplit-type ductless systems. For split-type ductless systems. HSPF shall be



## APF=

where: CLH= cooling load hours for a specific location as reported in Figure 1 of this appendix Q

..(95)=Steady state capacity as measured in Test A HLH=healing load hours for a specific location as reported in Figure 2 ofthis appendix defined as speCified in section 4.2.1 ofthis appendix. Separate values ofHSPF shall be determined for each combination ofindoor coils tobe used with a common outdoorcoil.

4.2.6 Heating seasonal performance foetorfor untestedcombinations ofsplitsystem centralairconditioners. (Reserved)

4.3 Annual performancefoetorforair-

source units. The annual performance factor (APF) shall beexpressed in Btu perwatthour: For each ofthe six regions in Table 2 of

.this appendix. a separate APF shall be determined for the standardized maximum DHR, the standardized minimum DHR and for all otherstandardized DHR's (See Table 3 ofthis appendix) between the maximum and minimum values. APF shall be defined as:



## [CLH 

# * 0ss(95)] 

## + 

## (HLH 

# * VHR 

# * C)

CLH 

# * 0S5(95)

SEER 

## HLB 

# * DHR 

# * C +

DHR=standardized design heating requirement C=adjustment factor which serves to adjust the calculated design heating load hours to the actual heating load hours experienced by a heating system and is 0.77 SEER= seasonal energy efficiency ratio as

. determined by 4.1 ofthis appendix 

## HSPF

HSPF=heating seasonal performance facto!

as determined by 4.2 ofthis appendix 4.4 Seasonalenergy efficiency ratiofor earth-coupledheatpumps andground water·

source heatpumps. The seasonal energy efficiency ratio (SEER) shall be expressed in Btu per watt-hour. For each of six regions specified in Table 4 ofthis Appendix. SEER shall be determined by:

SEER SEER (70)

- 70-T w • [SEER [70)-SEER (50)]

where: SEER(70)=SPLF' EER(70) SEER(50)=SPLF' EER(50) T" =ground water temperature for the respective region and is reported in Table 4 of this Appendix EER(70)=energy efficiency ratio at a ground water temperature of 70 OF. as determined bv 5.1.4.1a ofANSI/ARI Standard 32S.:.s5 EER(50)=energy effrciency ratio at a ground water temperature of50 OF. as determined by section 5.1.4.1b ofANSI/ ARI Standard 325-85

Where: HSPF (70) = SPLF • 3.412' COP [70) HSPF (50) = SPLF • 3.412' COP (50) 70-50

.

SPLF=seasonal part-load factor. and is assigned the value of0.90 4.5 Heating seasonalperformancefactor for earth-coupledheatpumps andground
water-source healpumps. The healing 8easonal performance factor [HSPF) shall be expressed in Btu per walt-hour. For each of the six regions specified in Table 4 of this appendix, a separate HSPF shall be determined for the standardized maximum DHR. the standardized minimum DHR and all other s.tandardized**DHR'~;** (See Table 3 of this appendix) between the maximum and minimum values.

70-Tw HSPF=HSPF(70)

- --. [HSPF(70)-HSPF(5O)] 70-50

Tw=ground water temperature for the respective region and is reported in Table 4 ofthis Appendix 4.5.1 Heating seasonalperformance factorfor units without supplementary resistance heat. For units without supplementary resistance heat. HSPF shall be defined as:

SPLF=seasonal part-load factor. ano IS assigned the value of0.85

### Federal Register 

# I Vol. 51, No. 194 

# I Tuesday, October 7, 1986 

# I Proposed Rules

COp(70)=coefficient ofperformance at a ground watertemperature of 10of. as determined by section SoU.lcofANSI/ ARJ Standard 3Z5-85

. COP(50)=c:oefficient ofperformance at a pund watertemperatureofSO of. as determined by IM!ction 5.l.5Jd ofANSI! ARI Standard 32S-85 3.412

# = conversion factor of3.412 Btu per waH-hour 4.5.2 Heating seasonal performance foetor for units withsupplementary resistanceheat. For units with supplementary resistance heat. HSPF shall be defined as lpecified in aection 10.2.2 ofANSI! ASHRAE Standard 116-1983. with the foUowing added provilioDl. One. the numberofhouri in

### the



### .JU' temperature bin (nJin the equations for HSPF andfor supplementary reaiatance heat
term (RH(t j )) shall be defined in4.2.1 ofthis appendix. Two. the heat pump low temperature cut-out factor shall be assigned the value of1.0. Three. the part-load ractor (PLF) shall be auigned the value of0.85. Four. the total powerinput (E(lj)) 

### shan be equal to the steady-state powerinput at a constant ground watertemperature (Ea(Tw)). which shall be defined as:

E..RCTw)=E..H(SO)

### +[&".H(70)

-**~.H(50)l** T..- 050

Where:

Ess .H(50)=steady-state powednput during heating at a ground water temperature of 50 ·F. as determined by section 5.l.4.1c ofANSI/AID Standard 325-85 E55 .H(70)=steady-state power input during beating at a ground water temperature of 70 ·F. as determined by section 5.l.4.ld ofANSIIARI Standard 325-85 Tw=ground water temperature for the respective region and is reported in Table 4 ofthis Appendix For regions I. II. 1II. IV and VI. the maximum DHR. the standardized DHR reported in Table 4 ofthis appendix. nearest to the greater ofeither Qss.H(Tw) or: DHRwAX = 2 Qss.dTw) * (55-ToD)
where:

T,....50 *--**7~50**

T

..



### -so *.-- Qss.dTw)=Qss.dSO)

### +IQss.d70) -Qss.dSO)]**7~SO** 

### 35757

### 35758 Federal Register 

# I Vol. 51, 

### No. 194 

# I Tuesday, October 1, 1986 

# I Proposed Rules

. TCID-outdoordes.temperature.

### as reported

...'.

. illTable

..ofthis AppaDdix

### /~SO)-steady-stateheatina capacityat a



### .**~.** 

### JIOIIIId watertemperature ofSO.,..

### as determined accordins to the

### testiDa requiremeJlts of5.1. 5.1.3and 5.1.4Jd of ANSII ARI Standard3Z5-85 Q...(7O)_steady-itate

### heatina capacity ata poundwatertemperature of70

.,..as determined accordiDs to the t

.. 

### tina requirementsof5.1. 5.1.3 and5.1.4Jc of ANSI/ ARI Standard3Z5-85 Q..dSO)-.teadY-Itatecoolin8capacityat a pound water_perature ofSO

.,..a. determined accordins to 

### the teatins requirements of5.1. 5.1.3 and s.u.lbof ANSI/ARI Standard**~** Q..d70)-steadY-Itatecoolinscapacityat a pound watertemperature of70 ·F. aa determined accordins to the testins requirements of5.1. 5.1.3 and 5.UJa of ANSI!ARJ Standard 325-85

. ForRegions I. U. Ul, IV and VI, the minimum DHR, which ia rounded offto the Dearest

### atandardiUd DHR reported InTable

..ofthis appendix. ia

### the

......ofeither Q...lT.)or:



# mm...

- Q..dT.) • (8&-T.J

ForRe,i0ll V. themaximum DHRia

### the peaterofeitherQ...(T.)or2.Z times

. Q..dT.)and 

### the minimum DHR

..the

### Jeuor ofeitherQ...(T.)or

### Q..dT .).Both

### thti maximum 

### and minimum values ofDHRare rounded offtotheDearest atandardized

### DHR reported InTable4 ofthia appeudix.

... Annual perfOrtlllUlCe

### foetorforIItUIh- .coUpledheot pumTm ond

### sroundwalBNDUrt:e heotpumTm. The annualperformance factor lAPP) aball beexpreued In

### Btu perwatt- '. bour. Foreach ofthe .Ixregions specified In Table4 ofthis appendix. a separateAPF ahanbe determined for eachcombination of OCR's and DHR's between and includins the maximum and minimum values. APF is defined as:



### [CLd * OCR) 

## + (HLH * DHR *C] 

### APF 

# =
eLH • OCR

SEER

vhere: Ui=cooling load hours for a specific location as reported in Table 4 ofthis Appendix HLH=heating load hours for a specific location as reported in Table 4 ofthis Appendix DHR=standardized design heating

. requirement C= adjustment factor which sel"\'es to adjust the calculated design heating load hours
to the actual heating load hours experienced by a heating system and ill 

### 0." SEER= seasonal energy efficiency ratio as determined by4.4 ofthis Appendix HSPF=heating seasonal performance factor

as determined by 4.5 ofthis Appendix For all regions. the maximum DCR is rounded offto the standardized OCR reported in Table 4 ofthis appendix nearest to Qss.dTwl. For region IV. the minimum OCR is the lesser ofeither Qss.dTwl or Qss.H(Tw ) dividp.d by 2.2. For Regions I. II, Ill. IV and VI, 

## + HLii 

# * OHR 

# * C



### dSPF

the minimum OCR is the lesserofeither Q..H(TW) or:

2 Qss.dTw) OCRWI = • (85-T OD] 60
4.7 Estimatedannualoperating costfor earth·coupledheatpumps andgraund watersourceheatpumps. For earth·coupled heat
pumps and ground water-source heat pumps. the cooling portion ofthe estimated annual operating cost (Ad at each design cooling requirement (OCR) for each region is:

CUi • DCR 

### Ac = • 0.001 • P SEER

where: CLH=representative average use cycle for cooling and is 1.000 hours OCR= as defined in 4.6 ofthis Appendix SEER= as defined in 4.4 ofthis Appendix D.OO1-converalOD factorofD.OO1 knowalt per watt P-repr

...... tIve averqeunitcoatof electricity ID doJJan perJcjJowatt-hour. aa provided purauant to 323(b)(2) ofthe Act

.**Por~pJed** heatpumps and

## iround
wateMourceheat

### pumpa. thebeatinsportion ofthe

.. timated annual 

### operatlns coat (Aa) at eachdesIp

### baatlns requirement (DHR) for _chrepmia:



### A..- HLH·DHR· C 

### *o.om.p

HSPF



### where:· HLH-repreaentatlve averap use cyclefor beatins and It2.0lIO hours DHR-aa defined In 4.8.1 ofthia Appendix Cea.defined In4.8.1 ofthis Appendix HSPF-aa defined In4.5 ofthis Appendix D.OO1-converaion factorofG.OO1 kilowatt per watt P-repreaentative average unit coat of electricity in dollars perkilowatt-bour, as provided pursuant to 323(b)(2) ofthe Act 4.8 Estimatedregionalannualoperating
cost foreorth-coupledheatpumps and groundwater-sourceheatpilmps. Forearthcoupled heatpumps andground water-source heat pumps, a 8eparate estimatedregional annual operatins cost shall be detennined for each combination ofItandardized design coolins and heating requirements between the maximum and minimum values. The estimated regional annual operatins cost shall be determined by the method in4.7 of this Appendix in which Tables 1. 2 and 3 of this appendix are used to determine the

. cooling load hours (CLH). heatinsload hours (HLH) and ground water temperature (Tw). Further. the seasonal energy efficiency ratio (SEER) and seasonal heating perfonnance factor (HSPF) are adjusted for the respective value ofTwin each region.

Table 1.-Oistribution of Temperature Bin Hours for Cooling

Bin No. (j).

1 _

.._ ............._ ...___.................. 2

..................._....._.__._ ............ 3

............._.__............._._ .... 4

................................_ ......___•... 5

.................._ ................_._....... 8

............._ .........._._. ___.._ .... 7._

.....__..._ ................__........ 8

........._ .........._ .._._........ Repr-. live Btn temperature (Tj)

67 72 

### n 52 87 12 17 102 Tempera. tureBin Hours

214 231 216 181 104 52 18 4

### Federal Register 

# I VoL 51, 

### No. 194 

# I Tuesday, October 7, 1986 

# I Proposed Rules

Teble

### 2.-DistrIJUtion 01Temperat1n Bin 

### Hoeft for Cooling



# ....... T

......... 1in HaIn

...

### ..n



# ....... 

# ..... lin

# No.. lin 

# ::rcr: I 

# • • " v VI**!~** 12 at.

# --,., 111 111 57 178 231 2411 250

# - .. 41 12 145 204 24t 232 231

# .,**~==** If1 17 178 240 2111 201

# .,

.., .t totO 231 22!1 214

# - J7 S1 110 208 245 2311 2111 7 12 14 70 t., 213 210 

# ..

---**~** 

# .. 30 112 'II 251 

# •**~O--==** 

# • 1 10 37 11M 204 

# •
17 0 

### a 

# ,. .t 15t 0 11

___ 12 0 0 

# • 

# • 121 0 ta...;...;._ 7 0 0 

# .. 21 '05 0 13..._.

__. 2 0 0 2 tC 

### eo 0 14

___ -3 0 0 0 5 50 0**t5~**___ 

# -. 0 0 0 2 28 0 te,.-- -t3 0 0 0 0 1C 0**1Tr_~_** -11 0 0 0 0 

# • 0 tlL

__._. . ':'23 0 0 - 0 0 3 0

Table**~.-Standardjzed** Design Cooling and Heating Requirements (Btu/hr)

5.000

......__ ........_ .................._.• 25.000 50.000 110.000 10.000

......_ ................__ ........... 30.000 60.000 100.000 15.000

......_._......_......_ ................ 35.000 70.000 110.000 20.000.............................................. 40.000 60.000 130.000

TABLE 4.-REGIONAL COOUNG LOAD HOURS

(CLH). HEATING LOAO HOURS (HLH). OUT·
DOOR DESIGN TEMPERATURE (Too) AND
MEAN GROUNO·WATER TEMPERATURE (Tw)

Region CLH HLH Too T.

I 2.COO 750 37 72 II 1.800 1.250 27 

### ee 

# '" 1.200 1.750 17 112 IV 800 2.250 5 63 V 

### coo 2.750 -10 45 VI 200 2.750 30 56 TABLE 

### I.-TEsT TOLERANCES FOR 

### 8T&ADY. STATE f'ERFOAMANcE 

### TEsTa FOR 

### ENmtCouPLED AND 

### GRouND WATEA-SouRctE HEATPuMPa 

# T_ T_



# ....... 0IIIdMaII 

# .!:

. 

# .... 

# -' _a

IndDor .,....." 'f: 

### a.o**~** tLI

IAIvinIJ U 1ndDor-.....,'f:**~.** 1.0 U

1MwInII· ,.0 0uId0cIr

.....IIuIb, 'f:**~** CUI U

1MwInII

.. CUI Water 1IcIw• ..-_ I E-..at ...-..nee 10

.. 1IcIw. inC:MI

01

.. ,.... _.

____ . 0.05 G.OI EJectric:8I '«III8Oa• ..- I.D

TABL.£ e.-EXPANSION DEvICE ScALING FACTOR. (F.) and Thermostatic Expansion Value Factor (F'l'Xv) for Matched Systems

Matched aystem F

....

TXV, no bleed

.......... TXV. no bleed

,....... 1,0

....._ ....... 1.000 TXV. no bleed

.......... TXV,

.. /bIeed

,......... 1.0

........._ ... 0.1175 TXV,

.. /bIeed

........... Tl(V, no bleed

,........ 1.0

............... 1.025 TXV, w/bleed

........... TXv,

.. /bIeed

, ......... 1.0

............... 1.000 CaptUary Of orifICe... TlCV, no bleed '

.._... 1.0

............... 1.050 Capillary Of orifoce... TXV, "'/bleed

,......... 1.0

............... 1.025 Capillary

.................... Capillary

.............._ ... Case I

......... 1.000 Capillary

.................... Onfice

........................ Case II

........ 1.000 Onfice

........................ Capillary

.........._...... Case III

....... 1.000 Onfice........................ Onfice....................... Case IV

....... 1.000

'The mixed TXV shall have equivaten\ capacity and

.. me euperhaat semng as the matclled TXV.

'The mixed TXV shall have equivalent capacity

.. the matched expansoon 0eYice.
[FR Doc. 8&-22486 Filed 10-6-86; 8:45 am]

..

LUNG CODE 1450-01-411 

### 35759