## "



## Thursday AprU**19~** 

## 1979



# Part II 

# Depart:ment of 

# Energy

Office oj: Energy Conservation and Solar' 

## Applications
Proposed Rulemaking and Public Hearing Regarding Test Procedures for' Central Air**Conditioners,~** 

## Including Heat Pumps23468 federal iRegister 

### f VoL 44, No. 77 

### f Thursday, April 19, 1979 

### I Proposed Rules

DEPARTMENT OF ENERGV



### . Office of Energy**ConselNalt~ol1l** WlIf1)(di



### Solar Applications
["10 

### CFR Part 430] 

### Proposed Rulemaking and PlIJJlblic Hearing Regarding Test Procecil.llres foll" Central Air Conditiol1lelrs, Ill1IcilUldlng Heat Pumps

AGENCY: 

### Department of ACTION: 

### Proposed rule.

SUMMARY: 

### The 

### ofEnergy hereby proposes to amend its test 

### procedures for central air conditioners 

### to include test procedures 

### for heat pumps. These test are of the energy conservation
consumerproducts pursuant to the Energy Policy and Conservation Act. Among other 

### the legislation requires methods oftesting be covered products. DATES: 

### Comments by 

### June 15, 1979; 

### requests to speak by June 1, 1979;**sta~ements** 

### by June 8, 

### 1979; hearing to 

### be held on June 13, 1979. ADDRESSES: 

### Comments and requests to speak at the hearing to: Margaret W, 

### Sibley, Conservation and Solar Applications, Department of

### Energy, Room 2221C, 20 Massachusetts Avenue, N.W., Washington, D.C. 20545.

Hearing held at: Department of 

### Energy, Room 2105, 2000 M Street, !\J,IN", 

### Washington, D.C. 20461. FOR FURTHER INFORMATION CONTACll':: 

### James A. Smith, U.S. Department of**Ener~,** 

### Office of Conservation 

### and

SolarApplications, Division of Buildings and Community Systems, Consumer Products Efficiency Branch. 20 Massachusetts Avenue, 

### N.VV., Washington, D.C. 20545, (2021 37&- 

### 4814. Margaret W. Sibley, U.S, Department of



### Energy. Office ofConservation and Solar Applications, 20 

### Massachusetts Avenue, N.W., D.C. 20545, (202) 376-1651. William

## J. Dennison, Office of 

### the

General Counsel, 20 Massachusetts Avenue, N.W

.. Room 3228, Washington, D.C. 20545. (202) 376- 

### 4100. SUPPLEMENTARY**INIFOlRiMftAT"O~:** 

### A. Background

On October 1,1977, the Department 

### of Energy (DOE) assumed the authority the Federal Energy Administration WEAl for the energy conservation program for consumerproducts, pursuant to Section 301 of the Department ofEnergy Act (DOE Act) 

### (Pub. L. 

### energy conservation program for consumer pwciucts was established FEA

I-'Uli DU'''''' to 

### Title

# m. B 

### the and Conservation Act**~~** n,v,. 

### Subsequently, the was the National Energy

Policy Act (NECPA) (pub. References in this notice to 

### "the or 

### to sections of the Act refer to the Energy Policy and Conservation Act as 

### emended by NECPA. Section 323 

### U.S.C. 6293) 

### of the Act 

### that standard methods of covered appear at 10



### Test procedures were 

### oe,')n.".,,,, central air conditioners 7,1977 (42 

### FR 30401, and a 

### test
air conditioners were November 21, 1977 November 25. 

### 19(7).

DOE is today proposing to amend the test procedures for central air conditioners to include for heat pumps, B. 

### Discussion

The heat pump is of

### air conditioner which mechanical refrigeration cycle to provide heating and may also cooling. DOE is proposing to include heal pumps as a class ofcentral 

### air conditioners because the function(s) ofthe equipment are essentialiy identical.

The definition ofcentral air conditioners is proposed to be modified to include both heating and cooling units. In order to clarify terms, definitions of "heat pump", "air-source heat pump", "water-source heat pump". and "cooling only unit", are proposed to 

### be added in Section430,2. Other new terms which specifically to 

### the laboratory methodology for performance are proposed to be included in Section 1 of 

### the proposed Appendix M.



### The lest methodology 

### for units remains the same as adopted for central air rOlnrli,tw,n 

### the organization of the test iI 

### appears in the Code of Regulations has been revised so 

### the heating performance methodology can be incorporated and the total
can be more understandable the
user. Sections 1, 2.1, 3.1, 4.1, 

### and 5.1 of proposed Appendix M 

### contain the test procedures for central'air conditioners as previously developed, while all other sections refer to new proposals heat pumps. The change to the central conditioner test procedure 

### the inclusion of the cooling seasonal pelrtolrm;3,nc;e factor (CSPF) in order io 

### maintain continuity between the proposed measure of and the measure ofcooling With this change, the measures may combined or weighted to an annual efficiency which may be used
consumers in purchasing decisions. that 

### the measure of in the energy standards for 

### centraJ air conditioners
on the cooling seasonal nprtn"'p",,n 

### factor (CSPF), the heating seasonal factor (HSPFj, or the annual performance factor These terms are defined 1.1,1.9, 

### and 1.15 

### of the proposed M. 

### the major additions have to do 

### only testing for performance, interested comment on the cooling as well as portion. Air-source heat pumps are equipped with a means ofproviding supplementary heat by means of electrical resistance or a fossil fuel furnace. These systems are at 

### low outdoor temperatures the heat itself cannot provide the 

### required

til> 

### satisfy the buildingload. It



### understood that the proposed rule as it 

### applies to air-source heat pumps only covers those units which are designed for use with electrical resistance back up systems. DOE is 

### currently developing test procedures for other types ofback up systems, including gas and oil furnaces, and intends to propose these as soon as practicable.

As described in the definition 

### of "'central air conditioner" only units which are electricallypowered are covered by these procedures. A

### vail.able information indicates 

### thai heat pumps and gas-fired conditioners are not distributed in
commerce to any significant extent and therefore are not included in this proposal.

Section 3Z3(a)(2) of the Acl 

### ."""nr"''' DOE to direct the National Bureau of Standards (NBS) to deveiop test procedures for the determination 

### ofthe estimated annual operating costs and at 

### least one other useful measure ofenergy consumption which DOE determines is likely to assist consumers in making purchasing decisions. At DOE's request NBS evaluated existing test proceciure§ for measuring energy consumption of 

### heat pumps. Present industry testingFedernl Register 

## I Vol. 44. No. 77 

## I Thursday, April 19. 1979 

## I Proposed Rules 23469

.


### procedures for heat pumps use steady state conditions and do not account for performance degradation due to defrosting and cycling ofthe unit

NBS transmitted to DOE a test TU',"r>,>rl,,,'P 

### review document which reviewed existing test procedures for measuring the energy consumption of heat pumps and which recommended a testprocedure. Copies ofthis review document will be made available for inspection by interested persons as provided for later in this notice,

The test procedure amendments recommended byNBS andproposed todayincorporate. in part. test procedures used by industryto measure the heating capacity and efficiency of heat pump equipment as described in 

### the Air Conditioning andRefrigeration Institute (ARI) Standards 240-77, 210-75, and 320-76 and the American Society of Heating. Refrigeration and Air Conditioning Engineers (ASHRAE) Standard 37-69. In addition. the amendments incorporateprocedures for determining estimated annual operating costs and seasonal performance factors ofheat pumps in both the heating and cooling modes.

Pursuant to section 301 ofthe DOE Act. DOE is required to comply with section 32'ofthe Federal Energy Administration Act of 1974 (FEA Act) (Pub. L. 93-275), as amendedby section 9 ofthe Federal Energy Administration Authorization Act of 1977 (Pub. L. 95- 70).

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

(a) If

### anyproposed rule by the Administrator contains any commercial standards. or specifically authorizes or requires the use ofany such standards. then any general notice ofthe proposed rulemaking shall:

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

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

(b) An organization complies with the requirements ofthis subsection in promulgating any commercial standards if:(1) it gives interested persons adequate notice ofthe proposed promulgation ofthe standards and an opportunity to participate in the promulgation process through the presentation oftheir views in hearings
or meetings which are open to the public;

(2) the membership ofthe organization at the time ofthe promulgation ofthe standards is sufficientlybalanced 80 

### as to allow for the effective**rel:l'rI~'St:[Jt!:itl(m** 

### ofan Interested persons; before promulgating such it

### makes available to th.e records or ofthe

UWl.cOUVU, 

### and anv letters.**memorandu~s.** 

### and materials relating to such standards; and

(4) it

### has procedures allowing interestedpersons to:

(A) obtain a reconsideration ofany action takenby the organization relating to the promulgation ofsuch standards, and

(B) obtain a review ofthe standards (including a review ofthe basis or adequacy ofsuch standards).

The findings required ofDOE by section 32 ofthe FEA Act serve to alert the public and DOE to the use and background ofcommercial standards in
a proposedrulemaking and, through the comment andhearing process, allow interested persons to make known their views regarding the appropriateness of the use ofthose particular commercial standards in that proposedrulemaking. Any negative finding does not reflect a determination by DOE ofthe advisability ofutilizing a particular standard for part ofthe testprocedure regulation.

As noted above, therulemaking proposed today contains elements of four commercial standards promulgated by two non-governmental organizations, ASHRAE and ARI.

Determinations have notbeen made regarding ASHRAE because the ASHRAE standard cited is part ofthe existing central air conditioner test procedure and was previously subjected to review under section 32(c) ofthe FEA Act. With respect to the ARI standards cited. DOE has determined that ARI does not comply with the requirements ofsection 32(b) because among other-- things, its membership is limited to manufacturers ofair conditioning and refrigeration equipment and. therefore is not "sufficientlybalanced so as to allow for the effective representation .ofall interested persons." As required by Section 32(c), DOE will consult with the Attorney General and the Chairman of the FederalTrade Commission concerning the impact ofthese standards on competition. prior to prescribing final test procedures. C. Measures ofEnergy Consumption

The Act requiresDOE to prescribe test proceduresfor the determination of estimated annual operating costs and at least one otherusefulmeasure ofenergy consumption which the Secretary determines is likely to assist consumers in makingpurchasingdecisions. DOE ift

### proposing to amend § 

### 430.22 suh£tltuting a newparagraph (m) to include all measures ofenerg"y consumption specified for an classes of central air conditioners including heat pumps. The fonowing is a brief

. description ofeach measure.

The estimated annual operating cost for the cooling and/orheating functions ofcentral air conditioners is an estimate ofthe electrical energy input necessary to satisfy a representative annual heating and/or cooling loadmultiplied by a representative average unit cost of electricity. For air-source central air conditioners (section 430.22(m)(1)). the annual electrical energy input for cooling is estimatedby dividing the output (the cooling capacity times the representative annual average cooling loadhours) by the seasonal energy efficiency ratio. The annualelectrical energy input for heating is estimatedby dividing the output (a representative design heating requirement times a representative average heating load hours) by a representative heating seasonalperformance factor. For watersource heatpumps (§ 

### 430.22{m){2n. the annual electrical energy input is estimatedby multiplying the test**m~asured** 

### electrical powerinput by the representative annual average cooling
orheating load hours.

Also proposed (§ 

### 430.22(m) (5) and (6))
as test procedures for the determination ofothermeasures ofenergy consumptionwhich are likely to assist
consumers in making purchasing decisions are test proceduresregarding the measures ofefficiency: The seasonal energy efficiency ratio, as described in 430.22(m)(5)(iv). the cooling seasonal performance factor. as described in 430.22(m}(5)(i) and430.22(m}(6)[i). the heating seasonal preformance factor. as described in 430.22{in)(5}(ii) and 430.22(m)(6)(ii), and the annual performance factor. as described in 430.22(m)(5)(iii) and430.22(m)(6)(iii). The cooling seasonal performance factor (CSPF) and the seasonal energy efficiency ratio (SEER) are an estimate ofthe total cooling output during the normal annual usage period for cooling, divided by an estimate ofthe total electric input during the same period. The heating seasonalperformance factor (HSPF) is an estimate ofthe total heating output during the normal annual usage period for heating. divided by an estimate ofthe totalelectric input during the same period. The annual performance factor (APF) is a weighted average ofthe combinedHSPF and CSPF depending on the number of annualheating loadhours and cooling23470 federal )Register 

## I Vol. 44, No. 77 

## I Thursday. April 19. 1979 

## I Proposed Rules .i


### loadhours for 

### a**SP€~cific** 

### region 

### ofthe proposedmeasures which
are likely to assist consumers in 

### purchasing decisions are the regional annual operating costs 

### for central air conditioners (§ 

### arid (4)). 

### The estimated regional**op~rating** 

### costfor the cooling and/or heating functions ofcentral air conditioners is an estimate of

### the annual .electrical energy input necessary to satisfy a local heating and/orcooling load multiplied by a representative average unit cost ofelectricity. The annual electrical energy input is 

### estimated in the same manner as detailed above except thatregional annual cooling and heating loadhours (from,sections 6.1.3. and 6.2.5ln AppendixM to Subpart B) 

### are performance factors described in 430.22(m} (5) and (6) are used.

DOE recognizes that there may be additional useful measures ofenergy consumption for central airconditioners otherthan the measures described above. Accordingly, today's proposed amendmentin paragraph430.22(m)(7) provides for other useful measures which the Secretary determines are likelyto assist consumers in.making purchasing decisions. These**measures~** 

### however. must be derived from the application ofthe uniform test method prGposed. today as Appendix- M 

### to 

### SubpartB. D. 

### Laboratory**M~thodoll!))gy**



### The proposed rule provides for a controlledlaboratory environment for measuring energy consumption of.all central air conditioners. including heat pumps. The test methodology for the airsource cooling mode is the same as adopted in the existing central air conditioner test procedure. Appendix 

### M has been renumbered with the aill'-
source coolingprotion ofthe test methodology appearing in sections 2.1. 

## :3.1. 4.1 and 5.1. Air-source heating test methodology appears in sections 2.2. 3.2. 4.2, and 5.2. Water-source heating and cooling methpdologies appearin sections2.4. 3.4. 4.4. 5.4, and 5.5. 

### All reference material is now incorporated in sections 6.1 through 6.4.

The proposed amendments specify methodologies for measuring the heating performance ofboth air-source and water-source heatpumps. The test method for air-source units in the heating mode utilizes four tests to evaluate: the steady state efficiency. the energy lost to defrosting the outdoor coil.**th~** 

### degradationeffect caused by 

### cycling ofthe unit. and the efficiency at low outdoor temperatures. UtHizingtbe results ofthesetests, an efficiency curve canbe generated which is 

### applicable to ail outdoor temperatures that may occur over the course of a heating season. A 

### mathematical summation technique is then used incorporating the weather data ofdifferent regions across the country to calculate the perfomance factors for a given unit in a particular iocation. Because an air-source heat pump has different performance depending on outdoor temperature. a 

### given unit will have varying performance depending on the geopraphicallocation ofthe unit

In 

### order to reduce the burden of increased testing onmanufacturers with limited capability for testing heating performance, an assigned degradation coefficient. Cn. maybe used in lieu of condicting the CyclicTest on air-source heat pumps. If

### this option is chosen the value substituted is proposed to be0.25 in all cases. The derivation ofthis factor is consistent with the present methodology used in the cooling performance testing. 

### Ifa manufacturer chooses this option. he must then use the assumed value in calculations for 

### all his basicmodels. Another technique used to reduce testing is the use ofa 

### faCtor to show improved seasonal performance onunits with sophisticated "demand-defrost control systems". Due to the complexity ofa test thatwouldbe required to show the actual difference in 

### seasonal performance between demanddefrost and the conventional timetemperature defrost systems. an estimated value of5 percent improvement in the defrost capacity was assigned to units which utilize demanddefrost control systems. This factor may be adjustedby DOE depending on data presented during the comment period. lEo RepresentativeAverage-Use 

### Cyde

Section 323(b)(2) (42 U.S.C. 6293(b)(2)) ofthe Act provides that testprocedures for determining estimated annual operating costs ofany coveredproduct shallbe calculated from measurement of energy use in a representative averageuse cycle and from representative average unit costs needed to operate such product during such cycle. DOE proposes that the original representative average-use cycle of 1000 

### cooling load hours peryearfor the cooling mode be applicable for both cooling only and heating/cooling units. DOE has also determined that 2080 heating load hours is the representative average-use cycle for central air conditioners in the heating mode. These determinations are basedupon NBS' recommendation. which in turnis based upon NBS' reports which estimated the annual compressor operatinghours for central air conditioners in 

### the cooling mode and the annual heating loadhours for 

### furnances. Because the average number 

### ofheating loadhours 

### is dependent on average weather data and the number of units in a given area, it

### is for
an types ofheating equipment f. Unit Costs ofEnergy

Under section 323(b)(2) 

### ofthe Act, DOE is 

### required to provide manufacturers with information on representative average unit costs of energy. This information was provided by notice issued July 11. 

### 1977 (42fR 36549. July 15, 1977) and is expected to be updated on a continuing basis, G. 

### Numberof 

### Units to beTested

On September 8. 1978. (43 

### FR 40192) DOE proposed to amend test procedures for 

### all types ofconsumerproducts including central air conditioners. currently coveredby this program, in orderto prescribe sampling provisions applicable to any testingrequired under section 323(c) or 324 ofthe Act. This testing relatedspecifically to representations regarding the energy consumption of or cost ofenergy consumedby the various products,and to the labeling ofthese products with eriergy consumption oforcost of

### energy consumedby the various products•.and to thelabeling ofthese products,with energy consumption information as required by the FederalTrade Commission {FTC).

DOE is today reproposing § 

### 430.22(m) to receive comments on the sampling approach to be adopted for central air conditioners. including heatpumps; The major proposed changes from the present sampling requirements include the use ofone sided sampling provisions in lieu oftwo sided. the use ofcomputer modeling mathematical correlation to rate the condenser-evaporator-coil combinations other than those actually tested, and the ability to substitute certain components within Ii 

### system 

### if
measures ofenergy consumption are not affected.

Those commenting on the September 8. 

### 1978. notice recommended that DOE adopt sampling plans which required fewer units to be tested as compared to either ofthe distinct plans presented in DOE's proposed sampling rulenrFIC's proposed labeling rule which appeared in the federal Register on July 21. 1978 (43 FR 31806).

The two rules proposed byDOlE and FTC wouldhave had different effects on the extent oftesting. The rule proposed byFTC specified thatunits ofevery basicmodel needbe tested. The ruleFederal Register 

### I Vol. 44, No. 77 / Thursday, April 19, 1979 /Proposed Rules 23471 

## = proposed by DOE contained provisions which had the effect of specifying that units of only certain basic models need be tested. Specifically, the DOE rule grouped basic models according to the condensing unit used andrequired that only units 

### ofthe condenser-evaporatorcoil-combination (defined in DOE test procedures) which was expected to have the largest volume ofretail sales among all basic models using that condensing unit need be tested. Both 

### the DOE and FTC proposed rules specified 90 

### percent confidence and toierances of 

### ± 5% 

### for their sampling plans, andboth utilized two-sided confidence limits.

Commenters requested that any sampling plan adopted should require the testing ofonly certainbasic models, and for those basic models tested, the statistical parameters should be modified to require fewer units to be tested as compared to eitherproposed rule.

Commenters provided information on the timerequired to test one unit; the frequency ofintroducing newbasic models; the number ofunits ofeach basic model which wouldhave to be tested to satisfy sampling provisions using modified samplingparameters; the extent that existing testresults can be used to fulfill the requirements of Federal program; the extent oftesting beyond the level previously conducted to support programs either administered by trade associations or conducted for the manufacturers' ownpurposes; the number ofbasic models the commenter currently produces; the energy consuming characteristics or features that distinguish the commenter's basic models; the capacity oftest facilities used by the commenter; and the cost of testing all the commenter'sbasic models,

Commenters urged that ifunits of every basic model were to be tested, testing costs could be expected to be $65 

### million. DOE has reviewed the data submitted and methods by which this figure was determined, and believes that actual costs wouldbe substantially lower, but may still be significant.

Commenters also stated that
measures ofenergy consumption of basic models net tested could be determined by engineering analysis based on data obtainedby testing other basic models which used the same condensing unit. It

### was argued that this method ofdetermining measures of energy consumption would be accompanied by very little sacrifice in reliability ofsuch measures. The DOE proposed sampling rule permitted the determination ofmeasures ofenergy consumption in this manner. Industrywide, the number ofbasic models which would require actual testing would be thus reduced by a factor of about 5, 

### with
a commensurate reduction in the costs oftesting. DOE is proposing that among all basic models using a single condensing unit, only units ofthe condenser-evaporator-coil combination expected to have the largest volume of retail sales need be tested.

Other comments indicated that DOE's proposed sampling plan was logically inconsistent in that it 

### specified confidence levels and tolerances for data not supportedby testing. DOE agrees that any simulation employing computer programs or engineering analysis to determine measures of energy consumption cannotreasonable demonstrate that the true mean ofsuch
measures is contained in a certainrange about represented values, Therefore ' today's proposedrules does not specify such confidence levels and tolerances for data not supported by testing. In order to provide manufacturers a guideline for determining measures of energy consumption applicable to all the units ofall basic models, The proposed rule describes certain minimum criteria for computer simulations which may be used in place oftesting certainbasic models, Whenever measures ofenergy consumption determined by computer simulation do not agree with measures ofenergy consumption determined by actual testing, the values determined by testing will be assumed to be the more reliable values,

The basis ofthe simulation technique must be a computer model ofthe mechanical vapor-compression refrigeration cycle, The major components in the refrigeration cycle
are modeled as "fits" to manufacturer component performance data. For example, heat transfer characteristics of the coils are modeled as functions of face area, number ofrows, air flow rate, fins per inch, and entering air enthalpy. Compressorperformance curves must be used to provide refrigerant mass flow rate and compressorpower as a function of suction temperature and condensertemperature. An iterative technique must then be usedwhich varies the evaporator temperature, condensing temperature, andrefrigerant
mass flow rate to balance the cycle. When the cycle is balanced, the enthalpies ofthe process endpoints are knows as well as the refrigerant mass flow rate, and, as a result, the measure ofsteady state efficiency can be calculated,

The computer model is then to be calibrated to actual test results and may be used to predict the energy efficieny of basic models which use the same condensing unit as a condenserevaporator-coil combination which has been tested. In order to insure the accuracy ofratings derived in this manner, and to insure compatibility between manufacturers, any manufacturer which uses the computer modeling provisions is required to submit to DOE a description ofthe analysis used, inchiding the computer model and the data and analysis used to verify the accuracy ofthe ratings obtained by computer modeling, At this time DOE does not plan to treat such information as confidential or proprietary, but is interested in receiving comments on this issue. DOE is also

,interestedinreceiving comments on the feasibility ofDOE prescribing a computermodel for use by all manufacturers who elect to rate their products in this manner.

Commenters stated that it

### is often necessary to substitute components manufacturedby different suppliers and '- that these substitutions typically have a minimal effect on energy consumption. Commenters further stated thatbased
on certain ofthe definitions ofthe term "basicmodel" presented in DOE test procedures, it 

### was not clear whether the units which include such component substitutions constituted a newbasic model which would require additional testing.

If

### the tested values ofthe measures of energy consumption for units having such component substitutions change by only a minimal amount from the tested values before the substitution, DOE agrees that additional testing ofsuch units would notprovide benefit to the
consumer commensurate with costs incurred, For example, if 

### a 350 watt condenserfan in a central conditioner is substituted for a 330 watt condenserfan and iflhis is the only design change which affects the tested values ofthe
measures ofenergy consumption, then the total average powerneeded to operate the unit may be expected to increase by 20 watts. However, as compared to the total average power consumption of4350 watts, any changes in the tested values ofthe measures of energy consumption wiil be less than
errors causedby the numerical rounding specified in DOE test procedures. Therefore, a sample ofunits containing the substituted condenser fan need not be tested since, bynot changing the values ofthe tested measure ofenergy consumption, the confidence statement remains satisfied for the represented values ofthe measures ofenergy consumption. However, if a 3500 watt compressor motor in a central airFederal Register 

### I Vol. 44, No. 77 

### I Thursday, April 19, 1979 

### I Proposed Rules



### conditioneris substituted for a 3300 watt compressor motorofidentical capacity, then the efficiency of such units is likely to decrease and their energy consumption is likely to increase, It

### is probable that the represented value of the measure of efficiency based on testing units containing the 3300 watt compressor motor will no longer satisfy the sampling confidence statement. In such case, further testing would be needed to establish the represented value of the measures of energy consumption which will satisfy the confidence statement for units which
use the 3500 watt compressor motor

To clarify the test procedures, wherever the term "basic model"' is used in § 

### 430.23, a footnote states that components of similar design may be substituted without necessitating further testing, ifthe represented values ofthe
measures ofenergy consumption will not change as a result of the substitution, i.e" the represented values continue to satisfy the sampling confidence statement. With the adoption of samplingplans utilizing one-sided confidence limits, manufacturers may adjust the represented values ofthe
measures ofenergy consumption from tested values of the measures of energy consumption to compensate for anticipated changes in the energy consuming characteristics offuture production units that may include such component substitutions,

After reviewing the data submitted, DOE by this notice is reproposing a samplingplan which specifies 90 percent confidence and 5 percent tolerances on a one-sided sampling system, DOE believes that this system provides the most reliable data for determining measures ofenergy consumption when compared against increased costs for testing,

An alternative approach under consideration by DOE is a pian in which manufacturers would be required to test two randomly selected units of the condenser-evaporator-coil combination likey to have the largest volume of sales. The measure of energy consumption used in labeling and representations would be required to be no higher than the mean of the values of efficiency derived from testing two units or no lower than the mean ofthe values of operation cost derived from the same testing. The advantage of this method would be to limit required testing to no more than two units.

Computer modeling would then be used for otherbasic models which use the same condensing unit. Manufacturers might still rate conservatively depending on their prior knowledge ofthe coefficient of variation of the particular product.

A disadvantage of this method is that the reliability 

### of the measures of energy consumption could be expected to be high for basic models where test results among the units tested show little variability. and the reliability could be expected to be low \",here there was substantial variability. It 

### should be noted that a major purpose for testing is to provide reliable measures of energy consumption in order to assist
consumers in making purchasing decisions.

Manufacturers and other interested persons are encouraged to comment on the proposed approach and the alternative. All comments and data pertaining to the alternate approach should be detailed specifically to provide a basis for incorporation into the final rule, in the event that the alternate approach is chosen for the final rule. H. Comment Procedure



### 1. Written Comment. Interested persons are invited to participate in this ruJemaking by submitting data, views or arguments with respect to the proposed amendments set forth in this notice.

Comments should be identified on the outside ofthe envelope and on documents submitted to DOE with the designation "Central Air ConditionersProposed Amendments (Docket No. CAS-RM-79-102)," Fifteen copies should be submitted. All comments received byjune 15, 1979, and all other relevant information. will be considered by DOE before final action is taken on the proposed regulation.

Pursuant to the provisions of 10 CFR 1004.11(e). any person submitting information which he believes to be confidential should so identify the information and submit one copy only of the information. DOE reserves the right to determine the confidential status of the information or data and treat it according to its determination.



### 2. PublicHearing. a. 

### Request Procedure-The time and place of the public hearing are indicated at the beginning ofthis preamble. The hearing will be continued, ifnecessary on June 14, 1979. DOE invites any person who has an interest in the proposed amendment issued today, or who is a representative of a group orclass of persons that has an interest in today's proposed amendment, to make a written request for an opportunity to make an oral presentation. Such a request should be directed to the address indicated at the beginning of this preamble and must be received before June 1. 1979. Such a request may be hand delivered to such address. between the hours of 8 

### a.m. and 4:30 p.m., Monday through Friday. A request should be labeled both on the document and on the envelope "Central Air Conditioners-Proposed Amendments (Docket No. CAS-RM-79- 102)."

The person making the request should brieflv describe the interest concerned: 

### if appropriate. state why she or he is a properrepresentative of a group or class ofpersons that has such an interest. and given a concise summary of the proposed oral presentation and a telephone number where she or he may be contacted through.

DOE will notify, before 4:30 p.m., June 4. 1979, each person selected to appear at the hearing. Each person selected to be heard must submit 15 copies ofher or his statement to the address and bv the date given in the beginning of this' preamble. In the event any person wishing to testify cannot meet the 15 copy requirement, alternative arrangements can be made with Margaret W. Sibley in advance of the hearing by so indicating in the letter requesting an oral presentation orby calling (202) 376-1651.

b, 

### Conduct ofHearing. DOE reserves the right to select the persons to be heard at the hearing, to schedule their respective presentations and to establish the procedures governing the conduct of the hearing. The length of each presentation may be Umited. based
on the number ofpersons requesting to be heard.

A DOE official will be designated to preside at the hearing. This will not be a judicial or evidentiary type hearing. Questions may be asked only by those conducting the hearing, and there will be no cross-examination ofpersons presenting statements. Any decision made by DOE with respect to the subject matter ofthe hearing 

### will be based on alJ information available to DOE. At the conclusion of all initial oral statements, each person who has made
an oral statement will be given the opportunity 

### if she or he so desires, to make a rebuttal statement. The rebuttal statements will be given in the order in which the initial statements were made and will be subject to time limitations.

Any interestedperson may submit questions to be asked of any person making a statement at the hearing to Margaret W

.. Sibley, Conservation and Solar Applications. DOE. 20 Massachusetts Avenue. NW., Washington. D,C. before 4:30 p.m. June 8, 1979, DOE will determine whether th(! question .is relevant, and whether the "',Federal Register 

## I Vol. 44. No. 77 

## I Thursday. April 19. 1979 

## I Proposed Rules 23473



### time limitations permit it 

### to be presented for answer.

Any further procedural rules needed for the proper conduct ofthe hearing will be announced by thepresiding officer.

A transcript ofthe hearing will be made andthe entire record ofthe hearing, including the transcript, will be retainedby DOE andmade available for inspection atthe DOE Freedom of Information Office in the Forrestal Building, Independence Avenue and L'Enfant Plaza, SW., Washington, D.C. 20585, betweenthe hours of8 a.m. and 4:30 p.m

.. Monday through Friday. In addition. any person maypurchase a copy ofthis transcript from the reporter. I. Environmental and Inflationary Review

Pursuant to Section 7(c)(2) ofthe Federal Administration Act of 1974. a copy ofthis notice has been submitted to the Administrator ofthe Environmental Protection Agency for his comments concerning the impact ofthis proposal on the quality ofthe environment. The Administrator has no comments at the present time.

The National Environmental Policy Act of 1969 requires DOE to assess the environmental impacts ofanyproposal issuedby the Department for "major Federal Slctions significantly affecting the quality ofthe human environment." Since test procedures under the energy conservationprogram for consumer products will be used only to standardize the measurement ofenergy usage and will not affect the quality or distribution ofenergy usage. DOE has determined that the action ofprescribing testprocedures. by itself. will not result in any environmental impacts. On this basis. DOE has determined that. with respect to prescribing test procedures under the energy conservation program for consumer products. no environmental impact statement is required.

The proposed rule has been reviewed in accordance with Executive Order 12044 and DOE Order 2030. From the regulatory analysis performed. it was -determined that the proposal was significant in nature but did not have major impacts to manufacturers and
consumers (imposing annual economic costs of$100 million or more). (Energy Policy and Conservation Act. Pub. L. 94-163. as amended by Pub. L. 94-819; Department ofEnergy Organization Act. Pub. L. 95-91; E.O. 12009. 42 FR 46267.)



### In consideration ofthe foregoing. it

### is proposed to amend ChapterII oftitle 10, Code ofFederal Regulations, as set forth below.

Issued in Washington. D.C.• April 6. 1979.
Omi G. Walden. Assistant Secretary, Conservation and Solar Applications.



### 1. Section430.2 is amendedby deleting the present definition of "central air conditioner" and "condensingunit" and adding the following new definitions inappropriate alphabetical order: § 430.2 Definitions. 

### * 

### * * *



### "Air-source heatpump" means a "heatpump" which consists ofone or more assemblies, which utilizes an indoor conditioning coil, compressor(s), andrefrigerant-to-outdoor-air heat exchanger to provide air heating. and whichmay also provide air cooling, dehumidifying. circulating, and air cleaning. 

### * * * 

### "Central air conditioner" means a consumer product which is poweredby single phase electric current. which is ratedbelow 65.000 Btu/hour, and which is either a "heatpump" or a "cooling only unit". * 

### * 

### * * *



### "Condensing unit" means a component ofa central air conditioner which is designed to remove the heat absorbed by the refrigerant and to transfer it

### to the outside environment, and which consists ofan outdoor coil, compressor(s), and air moving device.

"Cooling only unit" means a "central air conditioner" which consists ofa compressor(s). an air cooled condensing unit, and an evaporator or cooling coil. which is designed to provide air cooling, dehumidifying, circulating. and air cleaning. * 

### "Heat pump" means a "central air conditioner" which is either an "airsource heat pump" or a "water-source heatpump". *



### "Water-source heat pump" means a "heatpump" which consists ofone assembly which utilizes an indoor conditioning coil with air moving means. compressor(s), andrefrigerant-to-water heat exchanger(s) to provide both air heating and cooling, dehumidifying, circulating, and air cleaning. 

### * * 

### * *



### 2. Section 430.22 is amended by substituting a new paragraph (m) to read
as follows: § 430.22 Test procedures for measures of energy consumption. 

### * * * * *



### (m) CentralAir**Conditioners~** 

### (1) The estimated annual operating costfor cooling onlyunits and air-source heat pumps shallbe one ofthe following:

(i) For cooling only units or the cooling portion ofthe estimated annual operating costfor air-source heatpumps which provide bothheating and cooling. the product of(A) the quotient ofthe 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 ofAppendix M to this subpart, and the average seasonal energy efficiency ratio, in Btu's perwatthour, determined from section 5.1 of Appendix M to this subpart; (B) the representative average use cycle of 1000 cooling loadhours per year; (C) 

### a conversion factor of .001 kilowatts per watt; and (D) a representative average unit cost ofelectricity in dollars per kilowatt-hour as provided pursuant to section 323(b)(2) ofthe Act. the resulting product then being rounded offto the nearest dollarperyear;

(ii) Forheatpumps which provide only heating or the heating portion ofthe estimated annual operating costfor central air conditioners which provide bothheating and cooling. the product of (A) the quotient ofthe standardized design heating requirement nearest the capacitymeasuredin the High Temperature Test, Q

..(47) in Btu's per hour, determined in sections 5.2 and 6.2.6 ofAppendix M to this subpart. and the heating seasonal performance factor corresponding to the above mentioned standardized design heating requirement determined from section 5.2 ofAppendix M to this subpart; (B) the representative average use cycle of2080 heating load hours peryear; (C) 

### a correction factor

- described in section 5.2 ofAppendix M to this subpart; (D) a representative average unit cost ofelectricity in dollars perkilowatt-hour as provided pursuant to section-323(b)(2) ofthe Act; and (E) a conversion factor ofone kilowatt-hour per 3.413 Btu's, the resulting quotient then being rounded offto the nearest dollar peryear; or

(iii) 

### For central air conditioners which provide both heating and cooling, the quantity determined inparagraph (i) 

### above added to the quantity determined in paragraph (m)(l)(ii) above.

(2) The estimated annual operating cost for water-source heatpumps shall be the sum of:

(i) The product of(A) the electrical powerinput in watts, and described by the quantity EF in section 5.4 of23474


### AppendiXM 

### to'thisil'tlbpHri; {B} 

### the representative average use cycle of 1,000 cooling loadhoursperyear; (C) 

### a comrefslonfactorof.oolkilowattsper watt; and(j)) 

### a representative average unitcostof 

### electricityindollarsper kilowatt-hour asprovidedpursuantto section323(b)(Z) ofthe Act, theresulting product thenbeingroundedofftothe nearest

### t'Iollm-peryear, and



### iii}

### Theproduct

### of(A) the electrical**po~inputin** 

### watts, asdescribedby the quanti,tyEtJ in

### section 5.5

### of Appendix**~tothis** 

### subpart;{B}

### the representativeaverageuse cycle of2000 

### heatingloadhours peryear;,(C)

### a conversWn factor 

### of.001 

### kilowatts per watt; and 

### (D,arepresentative average trolt

### costafele.ctricity in 

### dollars per 'kilowatt-hour

### asprovidedpursuantto section:3Z3(b}(a).oftheAct. theresulting prodiJcr

### then being

### rounded offtothe nearestdollarper

### year.



## {:at The'estimated

### regional annual operatingOOst(s) 

### for coolingonlyunits and air-sourceheatpumps shaH beone of

### thefolloWing:



## til For;cooling 

### Qnly unitsorthe cooling portionofthe

### estimated annual operating cost for central air conditioners which provide both heating and,cooling.

### theproductof(A)

### the quotient of

### coolingcapacityin

### Btu'sper hourdetermined 

### from the steady-state wet-coiltest (testA) measured at the highestcompressorspeed. andthe averageseasonalenergy efficiency ratio in ,Btu's perwaH-hourboth determined from section 5.1 

### QfAppendix M 

### to this subpart; (B) 

### the estimatednumber of 

### local cooling

### load hours peryear determmedfromsection 6.1.3 of 

### AppendixM

### tothis subpart; (C) 

### a conversionfactor of .001 kilowatts per watt;and (D) 

### arepresentative average umtcostofelectricity indollarsper kilowatt-hourasprovidedpursuantto section323{b)(2) ofthe Act, theresulting produ:ct thenbeing rounded offto the nearesrdoHarperyear;

{ti}

### Fnrheatpumpswhich provide onlyheatingnrtheheatingporlinnofthe estimated annual operatingcostfor central'airconditionerswhich provide bothheating and cooling. for each applicable standardizeddesign heating requirement, the product of(A) the quotient9fthe estimatednumberof local heatingloadhours per year determirred from section13.2.5 of ApPendixM to this subpart. and the heating seasonalperformancefactor correspondingto the appropriate
standardizeddesign heating requirement determined from section 5.2 ofAppendix M to this subpart; (B) 0.77, a correction factordescribed in 

### section 5.2 of Appendix M to this subpart; {C) the standardizeddesignheatingrequirement in Btu?s perhour determined in secJi:ons 5.2and 6.2.6

### ofAppendix M 

### to this

,subpart; (D)

### a representative average unit cost of electricityin 

### dollarsper kilowatt-hour asprovidedpursuant to section 323(b}{2) ofthe Act; and {E) 

### a conversion factor ofonekilowatt-hour per 3,413 Btu's, the resulting quotient then being roundedoffto the nearest dollarperyear; or

.

(iii) 

### For central air conditioners which provide bothheating and cooling, 

### the quantity determined in paragraph (m)(3)(i) above added to each quantity determinedinparagraph (m){3}(ii) above,

(4) The estimatedregional annual operating costfor

### wat.er-source heat pumps shallbethe sumof:

(il Theproduct of(A) the quotient of the cooling capacityfrom test

### F inBtu's perhOllrandthe cooling seasonal performance factor as determined in section 5.4 ofAppendix M 

### to this subpartfor thelocalground water temperature determined from 

### section 5.4 and6.4 ofAppendiX M 

### to this subpart: (B) 

### the estimatednumber oflocal cooling loadhoursperyear determined from section 6.1.3 ofAppendix M 

### to this subpart; (C) 

### a conversion factor of

..293 watt-hours per Btu; (D) 

### a conversion factor of .001 kilowatts perwatt; and (E) 

### a representative average unitcost of electricity indGllarsperkilowatt houras provided pursuantto section323{b){2) of the Act, the resulting product thenbeing roundedoffto the nearestdollaryear, and

(ii) 

### The product of(A) the quotient of the heating capacityfrom test G, 

### inBtu's perhour, andtheheating seasonal performance factor as determined in section 5,5 ofAppendixMto the subpart for the local ground water temperature determined from section 5.5 and6.4 of AppendixM to this subpart; (B) 

### the estimated number oflocal heatingload hours peryear determined from section 6.2.5 ofAppendix M to this subpart; (C) 

### a conversionfactor of .293 watt-hours perBtu: {D} a conversion factor of .001 kilowatts per watt; and

## eE) a _ representative average unit cost of electricity indollars perkilowatt-hour
as providedpursuant to section 323(b)(2) ofthe Act. the resulting product then being rounded offto the nearest dollar peryear.

(5) The measure(s) ofefficiency for cooling only units and aiT-source heat pumps shanbe one ormore ofthe following:

(i) The cooling seasonal performance factor for cooling only units and airsource 

### heatpumps whichprovide cooling shall be the cooling seasonal performance factor determined according to section 5.1 ofAppendix'M to thi$ 

### subpart, rounded offto the 

### nearest

## a.m.

(ii) 

### TheheatiIlgseasonal performance factors for air-source heat pumps shall be the heatingseasonalperforffiance factors determined accordingto section 5.2 ofAppendixM 

### tothissubpart

### for each applicablestandardizeddesign heatingrequirementwithin each climaticregion, 

### roundedoffto the nearest0.01.



### rill] 

### The

### annualperformancefactors for air source heatpumps whichprovide heatingandcooling, shaH be the annual performance factors determined accordingto section 5.3.1 ofAppendix M 

### to this subpartfor each standardized design heatingrequirement within each climatic region, rounded offto the nearest0.01.



### (iv)The seasonalenergyefficiency ratio for cooling onlyunits and airsource heatpumps which provide cooling shanbethe 'Seasonal energy efficiencyfactorde!ermined according to section 5.1 ofAppendixM to this Subpart.roundedoffto thenearest (lOl.



### (6) The measurers) ofefficiency for water-sourceheatpumps shallbe one or more ofthe following: {i}

### The cooling seasonalperformance factors for watersourci'! heatpumps shallbethe cooling seasonalperformance factors determined according to section 5,4 

### of 

### Appendix M 

### to this subpart, rounded off to the nearest0.01.

(ii) 

### Theheating seasonalperformance factors for water-sourceheatpumps shanbe the heating seasonal performance factors determined according to section 5.5 ofAppendix M to this subpart, rounded offto the nearest0.01.

(ill) 

### The annual performance factors for water-source heatpumps shallbe the annual performance factors determined according to section5.6 ofAppendix M to this subpart for the local ground water temperature, cooling load hours andheatingloadhours, rounded to the

.nearest0.01. ' (7) 

### Otheruseful measures ofenergy consumption for central airconditioners shall be those measures ofenergy consumption which the Secretary of Energy determines are likely to assist
consumers in makingpurchasing decisions and which are derived from the application ofAppendix M to this subpart. * * 

### 3. Section 430.23 is amended by establishing a newparagraph (m) to read asfoHows:Federal Register 

## I Vol. 44. No. 77 

## I Thursday. April 19. 1979 

## I Proposed Rules 23475

§ 430.23 Unitsto be tested 

### * * (m)(l) For central air conditioners. each condensing unit shall have a basic model selected and a sample of sufficient size tested in accordance with applicable provisions of this subpart such that:

(i) Any represented value of estimated annual operating cost, energy consumption or other measure ofenergy consumption of a basic model for which
consumers would favor lower values shall be no less than the higher of (A) the mean of the sample or (B) the upper 90 percent confidence 

### limit ofthe true
mean divided by 1.05, and

(ii) Any represented value of the energy factor or other measure of energy consumption ofa basic model for which
consumers would favor higher values shall be no greater than the lower of (A) the mean of the sample or (B) the lower 90 percent confidence limit ofthe true
mean divided by .95.

(Z) The basic model 1 selected for tests shallbe that condenser-evaporator-coiIcombination likely to have the largest volume ofretail sales. For every other basic model 1 using that condensing unit, either-

(i) A sample of sufficient size shall be tested to insure that:

(A) Any represented value of estimated annual operating cost, energy consumption or other measure of energy consumption of a basic model for which
consumers would favor lower values shall be no less than the higher of (1) the
mean of the sample or (Z) the upper 90 percent confidence limit ofthe true
mean divided by 1.05 and

(B) Any represented value of the energy factor or other measure of energy consumption of a basic model for which
consumers would favor higher values shall be no greater than the lower of (1) the mean ofthe sample or (Z) the lower 90 percent confidence limit of the true
mean divided by .95. or

(ii) Represented values ofmeasures of energy consumption shall be based on a computer simulation of the energy consuming characteristics of such basic model. as described in paragraph (m)(4) ofthis section.

(3) The sample selected for paragraph (m)(l) ofthis section shall be comprised ofunits which are production upjts. or representative ofproduction units.

(4)(i) The basis 'ofthe computer simulation technique referred to in paragraph (Z)(ii) ofthis section shall be

I Components ofsimilar design may be substituted

... ithout requiring additional testing if the represented measures ofenergy consumption continue to satisfy the applicable sampling provision. a computer model of the,mechanical vapor-Compression refrigeration cycle. The major components in the refrigeration cycle shall be modeled as "fits" to manufacturer component performance data. Heat transfer characteristics ofthe coils shall be modeledas functions of face area, number ofrows, air flow rate, fins per inch, and entering 

### air enthalpy. Compressor performance curves shall be used to provide refrigerant mass flow rate and compressor power as a function of suction temperature and condenser temperature. An interative mathematical technique shall be used which varies the evaporator temperature, condensing temperature, and refrigerant mass flow rate to balance the cycle.

(ii) The computer model shall be calibrated to actual test results derived pursuant to paragraph (m)(l) of this section and may be used to derive
measures of energy consumption of other basic models which use the same condensing unit as the condenserevaporator-coil-combination actually tested. Any manufacturer who chooses to rate products by computer simulation shall submit to DOE a document describing the analysis used to derive such ratings. including the computer model. and the data and engineering analysis used to verify the accuracy of such ratings.

(iii) Whenever measures ofenergy consumption'determined by computer simulation do not agree with measures of energy consumption determined by actual testing, the values determined by actual testing shall be used to comply with section 3Z3(c) ofthe Act. or to comply with rules preflcribed under section 324 ofthe Act.

§ 430.24 [Revoked]

4. Section 430.Z4(m) is revoked. 5. Appendix.M to Subpart B ofPart 430 is amended to read as follows: Appendix MTo Subpart B-Uniform Test Method for Measuring the Energy Consumption ofCentral Air Conditioners 1, 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 "ARI" means Air-Conditioning and Refrigeration Institute.

1.3. "AR} Standard 210--75" means the test standardpublished in 1975by the ARI and titled "Standard for Unitary Air-Conditioning Equipment".

1.4 "ARI Standard 210-77" means the test standardpublished in 1977by the ARI and titled "Standard for Air-Source Unitaryheat Pump Equipment".

1.5 "ARI Standard 320-76" means the test standard publi$hed in 1976by the ARI and titled "Standard for Water-Source Heat Pumps".

1.6 "ASHRAE" means the American Society ofHeating, Refrigeration and AirConditioning Engineers. Inc.

1.7 "ASHRAE Standard 37-69" means the test standardpublished by ASHRAE in 1969 and titled "Methods ofTestingfor Rating Unitary Air-Conditioning and Heat Pump Equipment."

1.8 "Cooling load factor (eLF)" means the ratio ofthe total cooling done in a complete cycle ofa specified time period. consisting of
an "on" time and "off' time, to the steadystate cooling done over the same period at constant ambient conditions.

1.9 "Cooling seasonalperformance factor (CSPFj" means the estimated total cooling output ofa unit during its normal annual usage period for cooling divided by the total electric power input during the same period.

1.10 "Cyclic Test" means a test where the indoor and outdoorconditions areheld constant, but the unit ismanually turned "on" and "off' for specific time periodsto simulate part-load operation.

1.11 "Degradation coefficient (Cu)" means the measure ofthe efficiency loss due to the cycling ofthe unit

1.12 "Demand-defrost control system" me"ms a systemwhich is designed to perform the defrost function on the outdoor coll ofthe heatpump only when a predetermined degradation ofperformance is sensedby measuring the difference betweenthe outdoor airtemperature and the saturated refrigerant temperature leaving the outdoor coil. The control system is able to defrost at all frosting temperature conditions while compensating for pressure differentials
across the outdoor coil causedby factors other than defrosting.

1.13 "Design heating requirement (DHR)" is the amount ofheating required to maintaIn
a given indoor temperature at a particular outdoor design temperature.

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

1.15 "Heating seasonal performance !:actor (HSPF)" means the total hearing output of-a heat pump during its normal annual usage period for heating divided by the total electric power input during the same period.

1.16 "Heating load factor (HLF)" means the ratio ofthe total heating done in a complete cycle ofa specified time period, consisting of
an "on" time and "off' time. to the steady , state heating done over the same period at constant ambient conditions.

1.17 "Latent cooling" means the amount of cooling in Btu's necessary to remove water vapor from the airpassing over the indoor coil by condensation during a period oftime.

1.18 "Part-load factor (PLF)" means the
ratio ofthe cyclic energy efficiency ratio to the s1eady-state energy efficiency ratio at' identical ambient conditions.

1.19 "Seasonal energy efficiency ratio (SEER)" means the total cooling ofa central23476 Federal Register 

### I Vol. 44. No. 77 

### I Thursday. April 19. 1979 

### I Proposed Rules

air conditioner in Btu's during its normal annual usage period for cooling divided by the total electric powerinput in watt-hours during the same period.

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

1.21 "Single package unit" means any central air conditioner in which all the major assemblies are enclosed in one system.

1.22 "Split system" means any central air conditioner in which one or more ofthe major assemblies are separate from the others.

1.23 "Steady-state test" means a test in which all indoor and outdoor conditions are held constant and the unit is in a continuous operating mode.

1.24 "Temperature bin" means a 5'F increment over a dry-bulb temperature range of65'F through 104°F for the cooling cycle and _25°F through MOF 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 ofthe average ofthe test observations from the standard or desired test condition as provided in 6.1.1. 6.2.1. 6.2.2. and 6.2.3 ofthis Appendix.

1.27 "Test operating tolerance" means the maximum permissible difference between the maximum and the minimum instrument observation during a test as provided in 6.1.1. 6.2.1. 6.2.2 and 6.2.3 ofthis Appendix.

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. 

### Testing'Required

2.1 Testing required for airsource cooling onlyunits with single speedcompressors, two-speedcompressors, two compressors, or cylinder unloading. Two steady state wet coil tests required to be performed. test A and test B. Test A is to be conducted as an outdoor dry bulb temperature of95'F and test Bat 82°F. Tests C and D are optional tests to be conducted when cyclic performance parameters are to be measured in order to determine the degradation coefficient. Cn. Test Cis a steady state dry coil test conducted at an outdoor dry bulb temperature of82°F. Test Dis a cyclic test also conducted at an outdoor dry bulb temperature of82°F. In lieu ofcondUcting tests C and D, an assigned value of0.25 may be used for the degradation coefficient. Cn' Any manufacturer who chooses to use the ass.igned value must use it in calculations for all basic models.

2.1.1

.

### Testing required for units with single speedcompressors andsingle speed condenserfans. Test A and test B shall be performed according to the test procedures outlined in 4.1 ofthis Appendix. In addition. the cyclic performance shall be.evaluated by conducting test C and D according to the requirements outlined in 4.1 ofthis Appendix.



### 2.1.2 Testing required for units with single speedcompressors andmultiple-speed condenserfans. The test requirements for multiple-speed condenser fan units shall be the same as describeain section 2.1.1 for single speed condenser.fan units.



### 2.1.3 Testing required for units with twospeedcompressors, two compressors, or cylinder unloading. The test requirements for two-speed compressor units. two compressor units. or units with cylinder unloading are the
same as describedin 2.1.1 ofthis Appendix except that tes.t A and test B shall be performed at each compressor speed or at each compressor capacity.



### 2.1.4 Testing required for units with twospeedcompressors, two compressors, or cylinderunloading capable ofvarying the sensible to total(SIT) capacityratio. When a unit employing a two-speed compressor. two compressors. or cylinder unloading provides
a method ofvarying the ratio ofthe sensible cooling capacity to the total cooling capacity. (SIT). the test requirements are the same as for two-speed compressor units as described in 2.1.3 ofthis Appendix.



### 2.2 Testing requiredfor airsource heating onlyunits with single speedcompressors, two-speedcompressors, two compressors, or cyclinder unloading. Four types oftests are required to be performed: High Temperature, Cyclic, Frost Accumulation, and Low Temperature. In lieu ofconducting the Cyclic Test an assigned value of0.25 may be used for the degradation coefficient. Cn.



### 2.2.1 Testing required for units with single speedcompressors. Units with single speed compressors shall be subjected respectively to the High Temperature Test at 47°F described in section 3.2.1.1, the Cyclic Test as described in section 3.2.1.2. the Frost Accumulation Test as described in section 3.2.1.3. and the Low Temperature Test as described in section 3.2.1.4. Any manufacturer who chooses to use the assigned value must use it in calculations for all basic models.



### 2.2.2 Testing requiredfor units with twospeedcompressors, two compressors, or cylinder unloading. With the unit operating: at the high compressors speed (two-speed compressor), with both compressors in operation (two compressors), or at the maximum capacity (cylinder unloading); the follOWing tests are required to be performed
on all units; the High Temperature Test at 47'F, the Frost Accumulation Test, and the Low Temperature Test. An additional test (cyclic at47°F) is required, with the unit operating at the high compressor speed (twospeed compressor), with both «ompressors in operation (two compressors), or at the maximum capacity (cylinder unloading); if the normal mode ofoperationrequires cycling "on" and "off' ofthe compressor(s) at high speed ormaximum capacity.

With the unit operating: at the low compressor speed (two-speed compressor). with the single compressor which normally operates at low loads (two compressors), or at the low compressor capacity (cylinder unloading); the following tests are required to be performed on all units: the High Temperature Test at47°F, the High Temperature Test at 62'F, and the Cyclic Test. Additional tests, (Frost Accumulation Test and Low Temperature Test) are required. with the unit op.erating: on low compressor speed (two-speed compressor), with the single compressor which normally operates at low loads (two compressors) or at the low compressor capacity 1cylinder unloading), ifthe unit's low speed. one' compressor orlow capacity performance at andbelow 40°F is needed to calculate its seasonal performance.



### 2.3. Testing requiredfor air...source units whichprovide both heating andcooling;The requirements for units which provide both heating and cooling shall be the same as the requirements in Section 2.1 and 2.2 ofthis Appendix.



### 2.4 Testing requiredfor watersource units whichprovide both heating andcooling. The following four steady state tests, each employing two methods as described in 4.4,
are required to beperformed on all units: test E and testF as described in 3.4.1 and 3.4.3 of this Appendix and test G and test H as described in 3.4.2 and 3.4.3 ofthis Appendix.



### 2.4.1 Cooling testing requiredfor units with single speedcompressors. Two steadystate cooling tests, test E and test F. shall be performed according to the te.st procedures and test conditions outlined in 3.4 and 4.4 of this Appendix.



### 2.4.2 Heating testing requiredfor units with single speedcompressors. Two steadystate heating tests, test G and test H. shall be performed·according to the test procedures and test conditions outlined in 3.4 and4.4 of this Appendix.



### 2.4.3 Cooling testing requiredfor single speedcompressor units capable of modulating waterandrefrigerantflow to maintain constant capacity. The cooling tests required shall be the same as those detailed in 2.4.1 ofthis Appendix.



### 2.4.4 Heath1g testing requiredfor single speedcompressor units capable of modulating waterandrefrigerantflow to maintain constant capacity. The heating tests required shall be the same as those detailed in 2.4.2 ofthis Appendix. 3. Testing conditions



### 3.1 Testing conditionsfor airsource cooling onlyunits with single speed compressors, two-speedcompressors, two compressors orcylinder unloading. Th" test room requirement and equipment installation procedures are the same as those specified in sections 11.1 and 11.2 ofASHRAE Standard 37-69. Units designed for either horizontal or vertical installation shall be tested in the vertical upflow position. All tests shall be performed at the normal residential voltage and frequency for which the equipment is designed (either 115 or 230 volts and 60 hertz). the test installation shall be designed such that there will beno air flow through the cooling coil due to natural or forced convection while the indoor fan is "off'. This shall be accomplished by installing automatic dampers upstream and downstream ofthe test unit to block the offperiod air flow.

The following conditions listed in ARI Standard 210-75 shall apply to all tests performed in Section 3.1 ofthis Appendix: 5.1.1 Values ofthe StandardCapacity Ratings. 5.1.2 Values ofthe Standard Input Ratings.Federal Register 

## I Vol. _44. No. 77 

## I Thursday, .April 19, 1979 

## I Proposed Rules 23477

5.1.3 Values of the StandardEnergy Efficiency Ratio. 5.1.4.4 Cooling Coil Air Quantity. 5.1.4.5 Requirements for Separated Assemblies. 3.1.1 Testing conditionsfor units with single speedcompressors andsingle speed condenser fans. 3.1.1.1 Steady state wet·coilperformance tests (TestsA and Test B). Test A and test B shall be performed w;th the air entering the indoor side ofthe unit having a dry-bulb temperature of 80' F and a wet-bulb temperature of 67' F. The dry-bulb temperature ofthe air entering the outdoor side ofthe unit shall be 95' F in test A and 82' F in test B. The temperature of the air surrounding the outdoor side ofthe unit in each test shallbe the same as the outdoor
entering air temperature except for units or sections thereofintended to be installed only indoors, in which case the dry-bulb temperature surrounding that indoor side of the unit shallbe 80' F. For those units which reject condensate to the condenser, located in the outdoor side of the unit, the outdoor wetbulb temperature surrounding the outdoor side ofthe unit shall be 75'

### Fin test A and 65' F in test B.

3.1.1.2 Steadystate dry coilperformance test (Test C)andcyclicdry coilperformance test {TestD}. Test C and test D shall be performed with the air entering the indoor side ofthe unit having a dry-bulb temperature of 80° F and a wet-bulb temperature which does not result in formation ofcondensate on the indoor coil. (It is recommended that an indoor wet-bulb temperature of57° F or less be used.) The dry-bulb temperature ofthe air entering the outdoor portion of the unit shall be 82' F. The outdoor portion ofthe unit shall be subject to the same conditions as the requirements for conducting test B as statedpreviously in section 3.1.1.1. Test C shall be conducted with the unit operating steadily. Test D shall be conducted by manually cycling the unit "on" and "off." The unit shall cycle 1Nith the compressor "on" for 6 minutes and "off' for 24 minutes. The indoor fan shall also cycle "on" and "off', the duration ofthe indoor fan "on" and "off' periods being governed by the automatic controls which the manufacturer normally supplies with the unit. The results of tests C and D shallbe used to calculate a degradation coefficient. Cn , by the procedures outlined in 5.1 of this Appendix.

3.1.2 Testing conditionsfor unds with single speedcompressors andmultiple-speed condenserfans. The condenser fan speed to be used in test A shall be that speed which normally occurs at an outdoor dry-bulb temperature of95° F, and for test B, the fan speed shall be that which normally occurs at an outdoor dry-bulb temperature of 82' F. If elected to be performed, tests C and D shall be conducted at the same condenser fan speed as in test B.

3.1.3 Testing conditionsfor units with two-speedcompressors, two compressors, or cylinderunloading. The condenser fan speed used in conducting test A at each compressor speed shall be that which normally occurs at an outdoor dry-bulb temperature of95' F. For test B. the condenser fan speed at each compressor speed shallbe thatwhich normally occurs at an outdoor dry-bulb temperature of 82' F. Ifelected to be performed, tests C and D shall be conducted at the low compressor speed with the same condenser fan speed as used in test B. For those two-speed units in which the normal mode ofoperation involves cycling the compressor "on" and "off' at high speed, tests C and D shall also be performed with the compressor operating at high speed and at a condenser fan speed that normally
occurs at Test A ambient conditions. Units consisting oftwo compressors are subject to the same requirements as those units containing two-speed compressors, except that when operated at.high speed, both compressors shall be operating and when operating at low speed, only the compressor which normally operates at an outdoor drybulb temperature of 82' F shall be operating.

In lieu of conducting tests C and D, an assigned value of 0.25 may b used for the degradation coefficient, Cn at each compressor speed. lfthe assigned degradation coefficient is used for one compressor speed it must also be used for the other compressor speed.

In the case ofunits with cylinder unloading, the loaded and the unloaded conditions correspond to high and low compressor speed on two-speed units respectively.

3.1.4 Testing conditionsfor units with two-speedcompressors. two compressors, or cylinder unloading capable ofvarying the sensible to total (SIT) capacityratio. The mode ofoperation selected for controlling the SIT ratio in the performance of test A and test B at each compressor speed shall be such that it does not result in an operabng configuration which is not typical of a normal residential installation. Ifelected to be performed. tests C and D shall be conducted at low compressor speed (single compressor operating) with the same SIT control mode as used in test B when performed at the low compressor speed. Likewise, tests C and D shall also be conducted at high compressor speed (two compressors operating) and with the same SIT control mode as in testA when

. performed at the high compressor speed. In the case of units with cylinder unloading. the loaded and unloaded conditions correspond to high and low compressor speed on two-speed units respectively.

3.2 Testing conditionsfor air source heating only units with single speed compressors, two-speed compressors. two compressors. or cylinder unloading. "(he equipment under test shall be installed according to the requirements ofSection 11.2 ofASHRAE Standard 37-69 and Secbon 5.1.4.5 ofARI Standard 24077. Test chamber requirements are the same as given in Section 11.1 ofASHRAE Standard 37-39. Units designed for either horizontal or vertical installation shall be tested in the vertical upflow position. All tests shall beperformed at the normal residential voltage and frequency for which the equipment is designed (either 115 of230 volts and 80 hertz). 3.2.1 Testing conditionsfor units with singlespeedcompressors.

3.2.1.1 High temperature test conditions. The High Temperature Test at 47' F shall be conducted at an outdoor dry-bulb temperature of47° F and an outdoor wet-bulb temperature at 43' F_ The High Temperature Test at 62' F shall be conducted at an outdoor dry-bulb temperature of 62° F and an outdoor wet-bulb temperature of56.5° F. Forboth tests, the dry-bulb air temperature entering and surrounding the indoor portion of the unit shall be 70' F and a maximum wet-bulb temperature of 80' F. The duration of the tests shall be for a minimum of 'h hour.

3.2.1.2 Cycling test conditions. The Cycling Test at47' F shall be conducted at the same dry-bulb and wet-bulbtemperature
as the High Temperature Test at 47' F as described in 3.2.1.1. During the Cycling Test, the indoorfan shall cycle "on" and "off' as the compressor cycles "on" and "off', except that the indoor fan cycling times may be delayed due to controls that are normally installed with the unit. The compressor cycling times shall be 6 minutes "On" and 24 minutes "off." The test installation shallbe designed such that there will be no airflow through the indoor unit due to natural or forced convection while the indoor fan is "off." This shall be accomplished by installing automatic dampers upstream and downstream of t'le test unit to block the off period airflow.

3.2.1.3 Frast accumulatioIl testconditions. The dry-bulb temperature and dew-point temperature ofthe air entering the outdoor portion ofthe unit shall be 35' F and 30' F respectively. The indoordry-bulb temperature shall be 70° F and the maximum indoorwet-bulb temperature shallbe 80' F. The Frost Accumulation Test requires that the unit undergo a defrost prior to the actual test. The test then begins at defrost termination and ends at the next defrost termination. Defrost termination occurs when the controls normally installed within the unit
are actuated to cause it to change defrost operation to normal heating operation. During the test. auxiliary resistance heaters shall not be employed during either the heating or defrost portion of the test.

3.2.1.4 Lowtemperature test conditions. The tow Temperature Test shall be conducted at a dry-bulb temperature entering the outdoor portion of the unit of 17' F and a wet-bulb temperature of 15' F. The air entering the indoor portion ofthe unit shall have a dry-bulb temperature of 70° F and a maximum wet-bulb temperature of80' F.

3.2.1.5 Additionaltesting conditions. All tests shall be conducted at the indoor-side air quantities specified in Sections 5.1.4.3 and 5.1.4.6 and Table 2 ofARI Standard- 240-77. The following conditions listed in ARI Standard 240-77 shall apply to all tests performed in Section 3.2 of this Appendix: 5.4.4.4 Outdoor-SideAirQuantity: and 5.1.4.5 Requirementsfor Separated Assemblies. In all tests. the specified dry-bulb temperature entering the outdoor portion of the unit also applies to the air temperature surrounding the outdoorportion ofthe unit. Similarly, models where portions are23478 ,Federal Register / Vol. 44, No. 77 / Thursday, April 19, 1979 / Proposed Rules

intendedtobe installed indoors shall have theairtemperature surroundingtbatporiton ofthe rmit.the same as the indoor air temperature.**~** .

3.2.2 Testing conditions/orunits with two speedcompressors, two compressors or qylinder unloading. The testing conditions for two speed compressors, two compressors, or cylinderunloading shallbethe same as those for single speedunits,as described in 3.2.1.

3.3 Testing'coJiditionsfor airsource units whichprovide both heating andcooling. The testing conditions fOfunits which provide

,,both heating and cooling shall be the,same as

the requirements in Sections 3.1 and 3.2 of this Appendix;,'

3:4 Testing conditionsfor watersource unitswhichpravide both heating andcooling. The test to'om requirements and equipment installation...procedures are the same as those specified in Sections 11.1 and 11.2 of ASHRAE Standard 37-69. All tests shall be performed at the normal residential voltage and frequency for which the equipment is designed (either 115 or 230 volts and 60 hertz).

'3.4;1 Cuolingtesting conditionsfor units with singlespeedcompressors. TestE and

_test F shatlbe performed with the air entering

the indoor'side ofthe unit having a dry-bulb temperature ofBO° F and a wet-bulb temperature of67°F. The watertemperature enteringthe refrigerant-to-water heat exchanger on the outdoor side ofthe rmit shall be 85° F for testE and 60° F for testF. The watertliinperature leaving the refrigeranHo-water heat exchanger on the outdoor side ofthe unit shall be 95° F in test E. For test F, thetemperature shall be one which corresponds to the same flow rate as determined'in test E. The temperature ofthe air surrounding the unit in each test shall be BOO F.

3.4.2 Heating testing conditionsfor units with single speedcompressors. Test G and test H /lhall be'performed with the air enteriIlg the indoor side ofthe unit having a dry bulb temperature of70° F and a maximum wetbulb temperature of60° F. The water temperature entering the refrigerant-to-water heat exchanger on the outdoor side ofthe unit shall be 80' Ffor test G and 60' F for test H. Thewaterflow rate shall be the same as determined from test E and Fin 3.1.1 ofthis Appendix. The temperature surrounding the unit in each test shall be 70' F.

3.4.3 Cooling testing conditionsfor single speedcompressor units capable of lI/odulating waterandrefrigerantflow to maintiJin constant capacity. The same conditions as detailed in 3.4.1 shall apply except that no constraint shall be placed on the outlet, water temperature leaving the refrigerant-to-water heat exchanger in test E and test F.

,3.4.4 Heating testing conditionsfor single speedcompressor units capable of modulating waterand'refrigerantflow to maintain constantcapacity. Test G and test H shall beperformed with the air entering the indoor side ofthe unit having a dry-bulb temperature of70' F and a maximum wetbulb temperature of60' F. The water temperature entering the refrigerant-to-water heat exchanger on the outdoor side ofthe unit shall be 80° F with test G and 60' Ffor testH. The waterflow rate shall be determined bythe controls set by the manufacturer. The_control shall not be adjustedbetweenthe tests on the cooling performance and the test on lheheating performance.

4.0 Testingprocedures. Measure all electrical inputs as described in the procedures below. All electrical measurements shall include auxiliary power or energy (controls, transformers, crankcase heaters, etc.)delivered to the unit.

4.1 Testingproceduresfor airsource cooling onlyunits with single speed compressors, two-speedcompressors, two compressors, orcylinder unloading. All steady-state wet- and dry-coil performance tests on single package units shall simultaneously employ the Air-Enthalpy Method (Section 3ofASHRAE Standard 37- 69) on the indoor side and one othermethod consisting ofeither the Air-Enthalpy Method
or the Compressor Calibration Method {Section 40fASHRAE Standard 37-69) on the outdoor side. All steady-state wet- and drycoil performance tests on split systems shall simultaneously employ the Air-Enthalpy Method or the Compressor Calibration Method on the indoor side and the AirEnthalpy Method, the Compressor CalibrationMethod, or the Volatile Refrigerant Flow Method (Section 5 of ASHRAE Standard 37-69) on the outside. All cyclic dry-coil performance tests shall employ the Air-Enthalpy Method, indoor side only. The values calculated from the two test methods must agree within 6percent in order to constitute a valid test. Only the results from the Air-Enthalpy Method on the indoor side shall be used in the calculations in Section 5.1. Units shall be installe'd and tested in such a manner that when operated under steady-state conditions, the cooling coil and condenser coil air flows meet the requirements ofSections 5.1.4.3, 5.1.4.4, and 5.1.4.6 of Standard 210-75.

4.1.1 Test operatingprocedures. 4.1.1.1 Steady-state wet-coilperformance tests (TestA and TestB), Steady-state wetcoil performance tests [A and B) shall be conducted in accordance with the conditions described in sections 3.1.1.1, 3.1.2. 3.1.3, 3.1.4, and 3.1.5 ofthis Appendix and the procedures described for cooling tests in Section 11.3 of ASHRAE Standard 37-69 and evaluatedin accordance with the cooling-related requirements ofSection 12 ofthe ASHRAE Standard 37-69. The test room reconditioning apparatus-and the equipment under test shall be operated until equilibrium conditions are attained.

4.1.1.2 Steady-state andcyclicdry-coil performance tests (Test Cand TestD). The steady-state and cyclic dry-coil tests (C and D) shall be conducted as described below in accordancewith the conditions described in sectibns3.1.1.2, 3.1.2, 3.1.3,3.104, and 3.1.5 of this Appendix. The resultsshall be evaluated in accordance with the cooling related requirements ofSections 12.1.5, 12.1.6, 12.1.7, ofASHRAE Standard 37-69. The test room reconditioning apparatus and the equipment under test shall be operated until equilibrium conditions are attained, but not for less than one houi' before data for test C arerecorded. For all equipmenttest methods including the Comptessor CalibrationMethod, testC shall be performed with data recorded at 10- minute intervals until four consecutive sets of readings are attained with the tolerance prescribed in Section 11.6 ofASHRAE Standard 37-69. When theAfr-Entlialpy Method is used on the outdoor side for test C, the requirements ofthis section shall apply to both the preliminary test and the regular equipment test; the requirements of Section 3.6 ofASHRAE Standard**37~9** shall also apply. Immediately after test Cis completed, the test unit shall be manually cycled "ofP' and "on" using the time periods from 3.1.1 of this Appendix rmtil steadily repeating ambient conditions are again achieved in both the indoor and outdoor test chambers, but for not less than 2 complete "ofP'I"an" cycles. Without Iibreak in the cycling pattern, the rmit shall be run through an additional "off'/"on" cycle during which the test data required in 5.1 shall be recorded. During this last cycle, which is referred to as the tllsl cycle, the indoor and outdoor test room ambient conditions shall remain within the tolerances specified in 4.1.3 ofthis Appendix during the cyclic dry-coil tests, all air moving equipment on the condenser side shall cycle "on" and "ofP' when the compressor cycles "on" and "ofP'. Theindoor air moving equipment shall also cycle "ofP'
as governed by any automatic controls normally installed with the unit. This last requirement applies to units having an indo'or fan time,.delay. Units not supplied with an indoor fan time delay shall have the indoor airmoving equipment cycle "on" and "ofP' as the compressor cycles "on" and "off."

4.1.2 Test instrumentation. The steadystate and cyclic performance tests shall have the same requirements pertaining to instrumentation and data as those specified in Section 10 and Table II ofASHRAE Standard 37-69. For the cyclic dry-coil performance tests, the dry-bulb temperature ofthe air entering and leaving the cooling coil, or the difference between these two drybulb temperatures, shall be continuously recorded with instrumentation accurate to within ± 0.3',F ofindicated value and have a response time of 2.5 seconds or less. Response time in the time requiredfor the instrumentation to obtain 63 percent ofthe final steady-state temperature difference when subjected to a step change in temperature difference of 15' F or more. Electrical measurement devices (watt-hour meters) used during all tests shall be accurate to within 

### ± 0.5 percent ofindicated value.

4.1.3 Test tolerances. All steady-state**w~t-** and dry-coil performance tests shall be performed within the applicable operating and test condition tolerances specified in Section 11.6 and Table III ofASHRAE Standard 37-69.

4:1.3.1 The indoor**a~d** outdoor average dry-bulb temperature for the cyclic dry coil test D shall both be within 1.0' F ofthe indoor and outdoor average drybulb temperature for the steady-state dry coil test C.

4.1.3.2 The test·condition and test operating tolerances for conducting test Dare stated in 6.1.1 ofthis Appendix. Variation in**IF<edre~@lll lRregi£jae~**  

## ! 'if

### 01. 44, 

### No. 77 { Thursday, April 1il. 1979 

### I lProposed lRules

the tres! conditions than the tolerance6 inll.l.l this-Appendix ahaH the test. Itis suggested that an ,,!ectricresistance heaterhaving a equal to the sum co:m.pres,sOl: and i.nstalled 

### in

"'oft" arl€ll and "off' control in the mltcioot
an electric resistam;e
a heating capacHy to the cooling instal!ed in the

"on" and "off" al? the test unit cycles and "off' to hnprovB indoorroom control.

4.2 Testingproceduresfor airsource heatingonly units with single speed compre.ssors, two-speedcompressors, two compressors, orcylinderunloading.

4.2.1. Test operatingprocedures. 

### All High Temperature Tests. the Cyclic Test, the Frost Accumulation Test. and the LmN Temperature test shallhave the perfonnance evaluated the Air-Enthalpy Method em the indoor side. addition, the High Temperature Test and the Low Temperature Test shall have a simultaneous test method (as described in 4.1) used as 8 check. The values calculated from the two methods must agree within I)percentin order to constitute ill v8lid test. Only the results from the AirEnthalpy Method on the indoor side shall be used.in the calculations in section 5.2,

4.2.1.1 Testprocedureforhigh temperature test. When the outdoor Air-- Enthalpy Method isused. the outdoor chamber must not interfere with the norm81 air circulating pattern during the preliminary test. It is necessary to determine and adjust for system resistance when the outdoor air measuring apparatus is attached to the outdoor portion ofthe unit. The test room apparatus and test units must he operated for al least one hour with at least '!z hour at equilibrium and at the specified lest conditions prior to starting the test. The High Temperature Test shall then he conducted for
iii munimum of

### ¥2 hour with intermil!ent data being recorded at 10-minute intervals. For all units, especially those having controls which periodically cause the unit to operate in defrosl mode. attention should be given to prevent defrost during the High Temperature Test. Units which have undergone a defrost should operate in the heating mode for at least 10-minutes after defrost temination prior to the start ofthe test. When the outdoor AirEnthalpy Method is used as a second test. then a preliminary test must be conducted for
a minimum of30 minutes with 4 or more sets ofdata recorded at 10 minute intervals, all remaining requirements ofSection 3.6.1 in the ASHRAE Standard 37-69 shall then apply in conducting the preliminary lest for the outdoor air enthalpy method. For some units. at the ambient condition ofthe teet, frost may accumulate on the outdoor coil. ifthe air temperature or the difference between supply air temperature and the indoor air entering temperature has decreased by more than 1.5" F at the end ofthe test, the unit shaii 

### be defrosted and the les! restarted. Only the resulis ofihis second High TemperatureTest the heating seasonal O"l1rnrman,p''' "".,,'"'''''''''' in section 5.2. mol!'

beginnulg the High TemperatureTest. a in the mode for at after defrost termination to establish equilibrium conditions for the unH and the room reconditioniP..g The T ••ml,pf·"h"p Test when test and room are within the test condition tolerances 1.n Section 1l.2.1 ofthis Appendix.

4.2.1.2 Testproceduresfor the cyclic test. The cyclic test shall follow the High Tesland be cycled "on" and
as specified in 3.2.1.2 until steadily repeating ambient conditions are achieved for both the indoor and outdoor test chambers. butfor notless than 2 cOlnpl'ete "off'/"on" cycles. Without a breakin cycling pattern. the unit shall be operated through all additional "off'/"on" cycle, which the required test data shall be rp"nrn",i During the last cycle. which is referred to as the test cycle. the indoor and outdoor test room ambient conditions shall remain within the tolerance specified in section 1l.2.2. ofthis Apendix. If. prior to the High Temperature Test. the unit underwent iii defrost cycle to rid the outdoor coil of accumulated frost. then prior to cycling unit "off' and "on" it should be made to undergo a defrost. After defrost is compeleted and before starting the cycling process. the unit shall be operated continuously in the heating mode for at least 10 minutes to assure that equilibrium conditions have again been established for the unit and the room conditioning apparatus. Cycling the unit may begin when the test unit androom conditions
are within the High Temperature Test condition tolerances specified in section 6.2.1 ofthis Appendix. Attention should be given to prevent defrost after the cycling process has begun.

4.2.1.3 Testproceduresfor tbefrost accumulation test. The defrost controls shall be set at the normal settings which most typify those encountered in Region IV as described in section 6.2.4 and 6.2.5 ofthis Appendix. The test room reconditioning equipment and the unit under test shall be operated for at least % hourprior to the start ofa "preliminary" test period. The preliminary test period and the test period itselfare to be conducted within the test tolerances given in section 4.2.3.3 ofthis Appendix. In some cases. the preliminary defrost cycle may be manually induced. however, it is important that the normally operating controls govern the defrost termination in all cases. For units containing defrost controls which are likely to cause defrost at intervals less than onehour when the unit is operating at the required test conditions, the preliminary test period shall start at the terminalion ofa defrost cycle which aulomatically occurs and shall end at the termination ofthe next automatically occuring defrost cycle. For units containing defrost controls which are likely to cause defrost at intervals exceeding one hour when operating at the required test condition. the preliminary test period consists of "heatingonly" preliminary operation for at least one hour, after which a defrosl may be 

## ""HI'!''''} autornaltlC!ilIy induced, The**~e:st** at termination of defrost ends at the termination ofthe next**aumr[Ja'QlC~Ul~** occurring defrost cycle, 

### llfthe unithas not undergone II defrost after 12 hours, then the tests shall be concluded and the results calculatedfor this 12-hour 

### For units which tum the indoor flln defrost. the indoor supply duct shall be blocked during all defrost cycles to provent natural orforced convection through the indoorunit. During defrost. resistance heater§ normally installed with the unit shall be prevented from operating,

4.2.1.4 Testproceduresfor the low temperature test. Where applicable. the High TemperatureTestpreparation and performance requirements 

### shall also be used in the Low TemperatureTest.The test room reconditioning equipment shall first be operatedin a steady-state manner for atleast one-halfhour at equilibrium and at the specified test conditions.Theunit shall then undergo a defrost. eitherautomatic or manually induced. Itis important that the nnit terminate the defrost sequence by the action ofits own defrost controls. The defrost controls are

## to remain at the same setting as specified in 4.2.1.3. At a time" no earlierthan 10 minutes after defrost termination. the test shall start. Test duration is one-halfhour. For 

### all units. defrost should beprevented during the one-halfhour test period.

4.2.2 Test instrumentation. 4.2.2.1 Test instrumentationfor thehigh temperature test: Theindoor air flow rale shall be determined as described in Section 7.1 through 7.4 ofASHRAE Standard 37-69. This requires the construction ofan air receiving chamber and discharge chamber separatedbypartition in which one ormore nozzles are located. The receiving chamber)B connectedto the indoor air discharge"side of the test specimen through a short plenum. The exhaust side ofthe airflow rate measuring device contains anexhaustfan with some means to vary its capacity

# to obtain the desired external resistance to air flow rate. The exhaust side is then left open to the test room or is ducted through II " conditioning apparatus and then back to the test specimen inlet. The staticpressure across the nozzles. the veolcity pressure. and the static pressure measurements at the nozzle throat shall be measured with manometers which will result in errorswhich
are no greater than ±1.0percent ofindicated value and having minimum scale divisions not exceeding 2.0 percent ofthe reading. Staticpressure and temperature measurements mustbe taken at the nozzle throat in order to obtain density ofthe air. The areas ofthe nozzles shall be determined by measuring their diameter with an error no greater than ±O.2 percent in four places approximately 45 degrees apart. around the nozzle in each oftwoplaces through the nozzle throat. one at the outlets and the others in the straight section near the radius. The energy usage ofthe compressor. indoor and outdoor fan. and all other equipment components shall be measured with a walthour meter which is accurate to within ±0.5 ' percent ofthe quantity measured. Measurements ofthe air temperature entering23480 Federal Register 

## I Vol.. 44, No. 77 

### I Thursday. April 19, 1979 

### I Proposed Rule's

and leaving the indoorcoifor the difference between these two shall be made in accordance with the requirements of ASJ-IRi\,E Standard 41 part 1. These temperatures shallbe continuously recorded with instrumentation having a total system accuracy within ±O.39F ofindicated value arid a response time of2.5 seconds orless. Temperature measurements are to be made upstream of the staticpressure tap on the inlet and downstream ofthe staticpressure taps on the outlet. The indoor and outdoor dry-bulb temperatures shall be continuously recorded with instrumentation which will resultin an errorno greater than ±0.3"F of indicated value. The outdoor wet-bulb temperature shall be continuouslyrecorded. Static pressure measurements in the ducts and across the unit shallbe continuously recorded. Staticpressure measurements in the ducts and across the unit shall be made in accordance with Section 8 ofASHRAE Standard 37-69 using a manometerwhich will result in an error nogreater than ±0.01 inch ofwater. All other data not continuously recorded shall be recorded at 10minute intervals.

4.2.2.2 Test instrumentationfor the cyclingtest. The air flow rate during the onperiod ofthe CyclicTest shall be**~e** same agreewithin ±1.percent} as the airflow rate measured during the previously conducted Hiah TemperatureTest.All other in:trumentatioilrequirements are identical to 4.2.2.1 ofthis Appendix.

4.2.2.3 Test instrumentationfor thefrost accumulation test. The airflow rate for the Frost AccumulationTest shallbe the same as described in4.2.2.1. The indoor-side dry-bulb temperature and outdoor-side dry-bulb temperature shallbe continuouslyrecorded with ins'trumentation having a total system accuracy within ±O:3"F ofindicated value. The outdoordewpoint temperature shall be measured with an errornogreater than ±OSFofindicated value using continuously recording instrumentation.,All other data shall be continuously recorded at 10minute intervals during the heating cycle. Defrost initiation. termination and complete test cycle time (from defrost termination to defrost termination) shall be recorded. Defrost,initiation is defined as the actuation [either automatically ormanually) ofthe controls normally installed with the unit which cause itto alter its normal heating operation in order to eliminate possible accumulations offrost on the outdoor coil. Defrost termination occurs when the controls normally within the unit are actuated to change from defrost operation to normal heating operation. Provisions should be made
so that instrumentation is capable of recording the cooling done during defrost as well as the total electrical energy usage during defros.1. These data and the continuouslyrecorded data need be the only data obtained during defrost.

4.2.2.4 Test instrumentationfor theJaw temperature test. Instrumentation for the Low Temperature Test is identical to that ofthe High Temperature Test described in section 4.2.2.1 ofthis Appendix.

4.2.3 Test tolerances. 4.2.3.1 Test tolerancesfor the temperature test. All tests shall be conducted within the tolerances specified inSection 6.2.1. Variation greater than those given shall invalidate the test. The heating results by the indoor Air Enthalpy shall agree within 6 percent of the value determined by any other simultaneously conducted capacity test in order for the test to be valid,

4.2.3.2 Test tolerancesfor the cyclic test. The test condition**toleran~es** and test operating tolerances for the on-period portion ofthe test cycle are specified in Section 6,2.2. Variation exceeding any specified test tolerance shall invalidate the test results.

4.2.3.3 Test tolerancesfor thefrost accumulation test. Test condition and test operating tolerances for Frost Accumulation Tests are specified in Section 6.2.3. Test operating tolerances during heating applies when the unit is in the heating mode. except for the first 5 minutes after the termination of
a defrost cycle. Test operating tolerance during defrost applies during a defrost cycle and during the first 5 minutes after defrost termination when the unit is operating in the heating mode. In determining whether the test condition tolerances are met, only the heating portion ofthe test period shallbe used in calculating the average values. Variations exceeding the tolerances presented in Section 6.2.3 shall invalidate the test.

4.2.3.4 Test tolerancesfor the low temperature test. During the test period for the Low Temperature Test, the operating conditions shall be within the tolerances specified in Section 6.2.1 ofthis Appendix.

4.3 Testingproceduresfor airsource units whichprovide both heating andcooling. The testing procedures for units which provide both heating and cooling shall be the
same as those specified in Section 4.1 and4.2 ofthis Appendix. Also during the off-period ofthe dry-coil cooling test (test D). the switch-over valve shall remain in the cooling mode. unless the controls normally supplied with the unit are designed to reverse it. in which case the controls shall operate the valve. During the off-period ofthe cyclic heating test at 47'F. the switch-over valve shallremain in the heating mode, unless the controls normally supplied with the unit are designed to reverse it. in which case the controls shall operate the valve.

4.4 Testingproceduresfor watersource units whichprovide both heating andcooling. All steady-state heating and cooling performance tests on units shall Simultaneously employ the Air Enthalpy Method [Section 6 ofASHRAE Standard 37- 69) on the outdoor side.

4.4.1 Test operatingprocedures. All heating and cooling performance tests shall be conducted in accordance with the procedures in Section 11 ofASHRAE Standard 37-69 and evaluated in accordance with the related requirements ofSection 6 and 12 ofASHRAE Standard 37-69.

4.4.2 Test instrumentation. The heating and cooling performance tests shall have the
samerequirements pertaining to instrumentation and data as those specified inSeclion 10 and Table II ofASHRAE ££ ,m71
Standard 37-6.9. Units shall be installed and tested in soch a manner that when operated**d~"ltlv-':t"i!"** conditions, the cooling condemser air flows meet the of Sections 5,1.'1.3 and 5,1.4.5 Standard 32G-7ft 4.4.3 Test tolerances, AU**r.n~fn"~~n,r"** tests shall be "PFlllnll"'!! within applicable operating condition tolerances specified in Section 11.6 and Table In ofASHRAE Siandard 37-00,

n.O Caicujatjonsforperformancefactors. 5.1 CalcuJaUons ofcooling seasonal peliormancefactars (CSPF) andseasonal energy effjciencJi raUos (SEER) in air-source units.

The testing data and results required for these calculations shall include the following:

(i) Cooling capacities (Btu/hr) from tests A and B and, if applicable, the cooling capacity (Btu/hr) from test C and the total cooling done from test D (Btu·s). 

## Oss" (95F) 

## Ossk [82F) 

## Os., dry 

### Qcyc, dry

(il) Electrical power input to all components and controls (watts] from tests A, B. and ifapplicable the electrical power input to all components and controls (watts) from testC and the electrical usage (walthour) from test D.**~**..

k [95F) E

..k (82F) Essk, dry 

## E.".co dry

[iii) Indoor air flow rate (SCFM) and external resistance to indoor air flow (inches ofwater).

(iv) Air temperature (oF) Outdoor dry bulb Outdoor wet bulb Indoor dry bulb Indoor wet bulb

Where the cooling capacities 

### Q

..k [95FJ. from test A. 

### Qssk (82), from test B. and

## 0

.., dry. from test C. are calculated using the equations specified in section 3.7 ofASliRAE Standard 37-69. The total cooling done. Qcyc' dry from test D. is calculated using equation (lJ below.

Units which do not have indoor air drculating fans furnished as part ofthe model shall have their measured total cooling capacities adjusted by subtracting 1250 Btu/ hr per 1.000 CFM ofmeasured indoor air flow and adding to the total steady-state electrical power input 365 watts per 1.000 CFM of measured indoor air flow.

.**~** Energy efficiency ratios from tests A. B, and C. EERA• EERs, and

### EER.•. dry respectively. are each calculated as the ratio ofthe total cooling capacity in Btu/hrto the total electrical power input in watts.

Units which do not have indoor air circulating fans furnished as part ofthe model shall adjust their total cooling done and energy used in one complete cycle for the effect ofcirculating indoor air equipment power. The value to be used for the circulating indoor air equipment power shall be 1250Btu/hrper 1.000CFM ofCirculating indoor air. The energy usage required inone complete cycle required for indoor air circulation is the product ofthe circulatinguv
indoor air equipment oftime in one cycle indoor air 

## """l"fJ'"'''''' done shall

test cycle. federal IRegEster. 

## ! Vol. 44. No. 77 

## I Thursday, April 19. 1979 

## I Proposed Rules

efficiency ratio from. D, ElEl'-o,c, dfv is as the ratio of total co"oliag done in Btu's to the total el.ectrical energy usage in**1NaH-llOur,~,** 1!l!IiLlUltiG CODE M5tHll-i!11 23481

### CAS-RM-79-102 COMMENT 01

Federal Register 

### I Vol. 44. No. 77 

### I Thursday, April 19, 1979 

### I Proposed Rules



### The results of the cyclic ?rrl**~·p·~~-sttte** 

### dry-coil performance tests shell bfi! llSI'" ;P 

### the 

### fo11o\<,;ng (11) 

### eauations:

(l)



### where 60 

### x 

### T x Cpa 

### x Cl

### eye ; dry'" [V

### n • x (1 

### + \4

### n)]



### Ocyc,dry



# v

Cpa

V

### n' 

### ., Total con1 in" 

### ever 1:. 

### ctcl" cO'isi5tin'1 01' 

### one compressor**"~ff·** 

### period and**on~** 

### comnressor "on" aerior (Rtu'sl 

### Indr:'or eir**~lr\"** 

### rate (cf!) at 

### the dry-bulb temperature. humidity ratio. and pressure existing in the reninn 0f**~easure~ent.**


### • 5necific heat !t constant rressure of airwater mixture ner nrund nf 

### dr· t 

### air, (Btu/lb-°F). " Specific voluJ11e of air-,,'atPr**r~;y.ture** 

### at

the same dry-bulb**tf"-'-,ril.~ure.** 

### humidity ratio. and '1rf'SS'IrE' used in the determinati0n rf '::\(' i'ldrnr**~ir ~10'"**  

### rilte (ft3/lb).

1;1 " 

### Humidity ratio (lb/lb). and 

## r**~hr.-OF),** 

### which is described by the equation:
(2)



### whereTal (t)



### Ta2 (t) 

### ((time indoor fan off) 

## r 

# "J (lhfle 

### indoor fan on)

" Dry bulb**tem~ercture** 

### of air enterin" tJ-.o



### indoor coil (l'F) 

### :ot time (t). 

### " Dry-bulb**ter.~0roture** 

### of air**leavin~** 

### the

indoor coil (oF) at time (t). (3)



### where
ClF QCYC, 

### dry elF" 

### Qss dry 

## x T



### : cooling load factor. Qss dry = 

### Total steady-state coolinq capacity from test 

## C (Btu/hr).

= 

### Duration cf time (hours) for one completa cycle cnnsistino of one compressor "on" ti!"e ilnrl**or~ cnmDres~or**  

### "off" time.
The 

### oroceding equatiors**a\"~** 

### then**us~r\** 

### in 

### the followinq equatlon to calculate a degradation coefficient CD rounded to the nearest 

### .01.

.

(4) 

### 1

_ EERcyc,dry EERss,rlry 1

- ClF

whereEERss,dry= Energy efficiency rat;('l froPl**~est** 

## r, (Btu/watt-hr) •

### CAS-RM-79-102 COMMENT 01

federal Register 

### I Vol. 44. No. 77 

### I Thursday. April 19. 1979 

### I Proposed "Rules

Calculate the cooling seasonal performance factor (CSPFl
for air source central air conditioner or heat pump.

where:
SEER

3.413 SEER CSPF

.. 3.413

the seasonal energy efficiency ratio as determined
in section 5.1.1. 5.1.2. 5.1.3. or 5.1.4 below.

a conversion factor which converts watt-hours

to Btu·s. 

### 5.1.1**~ethod** 

### f,r calcu1utinn > 

### SErR for units with single-speed comnressor and sinr.1e**~n~ed** 

### condenser fans. The seasonal energy efficiency ratio for units employin!) single-speed compressors and single-speed condenser fans shall be based on the performance of**te~t** 

### Band a method outlined in 2.1.1 and 

### 3.1.1 of this Arnendix to account for the cyclic performance.
The seasonal energy efficiency ratio in**Btu's/Vlatt-hou~** 

### shall be determined by the equation:

where

where 

### SEER = 

### PLF (0.5) XEERS

EERB Energy efficiency ratio determined**fro~** 

### test C as oQt1ined in 2.1.1 PLF(O.5)= Part-load performance factor determined from the equction: 

### PlF (0.5) 

## = 1

- Co 

### (1-n.3)

= 

### Is the degradation coefficient described

in 2.1.1 or as calculated in e0uation (4) 

### above

5.1.2 'lethod for calculating a 

### SEER for units with sing1e- speed compressors and multi-speed condenser fans. -he seasonal energy efficiency ratio 

### (SEER) for units**e~nloying** 

### single-speed compressors and multi-saeed condenser**"~ns** 

### shall be based on the energy efficiency ratio obtained for test 

### Band the method outlined in 2.1.2 of this Apnpndix to account for the performance under cyc1 ic condition!". The energy efficiency ratio for test B 

### is obtained witr. tOle unit operating with the condenser fan speed which nOrMal'" occurs at test B ambient conditions. The seasonal energy efficiency ratio i!' 

### Ptu'sf"att-hour shall be determined by" the equation:

where 

### SEER = 

### PlF (0.5) XEERr,

erpr"

.. e"ficiency ratio determined from**tp~':** f>. 

### in 2.8
Part-load performance factor as determined from the equation:**~Lf** 

### ,U.b) 

# = I

- LO (I

- 

### 0.5)

### CAS-RM-79-102 COMMENT 01

23484 Federal Register 

### I Vol. 44. No:77 

### I Thursday. April 19. 1979 

### I Proposed Rules



### where The**desrad~tion co~fficient**  

### described in 2.1.2 or as calculated in enuation (4) 

### above.
5.1.3 tlethod for calculatinq a SE":P. fer units**~Iith** 

### t,·'o speed compressors or blo compressors, or cyl inder unloadinq. The calculation orocedure described in this section shall be based on the performance of test fl, 

### and B 

### at each of the compressor soeeds for two-speed compressor units, subject to the conditions on condenser fan sneed described in 3.1.3.

. Units operating with two compressors shall have the SEER calculated in the same manner as two-speed compressor units. The superscripted index k=l, (and the term "low-speed") designates the compressor that normally operates at an outdoor dry-bulb temperature of 820 F 

### and k=2 (and the term "hioh snee{''') denotes**o~eration** 

### with both compressors. '
In order to evaluate the steady-statecaoacity Qssk(Tj), and power input, E"ssk(Tj)' at tel'1perature Tj for each comoressor speed, k=l, k=2, the results of tests 

## Aand 

## Bfrom 5.1 shall be used in the followinq equation:

.

Qssk (Tj) = Qssk (95 F)



### where+ 

### 0ssk(82 F)

- 

### Qssk(95 F) 

### 95

- 82 [33-(5 Xj)]



### Steady-state capacity measured from**t~st** 

## Aas outlined in 2.1.3. Steady-state capacity measurep frnm test B as outlined in**2.1.~.** 

### EsSk(Tj)**~ ~k(95**  

### F)

+ 

### Essk(82 F}

- 

### Essk(95 F) [33

_ 

### (5 X 

### i)] 95

- 82


### vlhen
Electrical power input measurpd usinq test 

## Aas outlined in 2.1.3.

= Electrical power input measured from using test 

## Aas outlined in 2.1.3. The building coolino load.• Bl(Ti) for the four cases described in section 5.1.3.1 

### through 5.1.3.4 

### sha11 

### be obtained from the following equation:

)'Ihere (5Xj)

- 3

-= 

### 95

- 65**Qs~=2** 

### (95 F) it 

## 1.1



# = Steady-state capacity measured**+ro~** 

### test 

## A in 2.9 at the hiqh compressor speed.
The value of the degradation coefficient CDk =1 for low compressor speed cycling and CDk=2 for hiqh**s~eed** 

### on/off compressor cycling is determined as described in section 2.1.3, or as calculated above in equation 

## (1).
5.1.3.1 Units operating at low compressor speed (k=l) for which the steady-state cooling capacity, Qssk=l(T,i), is greater than or equal to the building cooling load, Bl(Tj). evaluate the following equations:

(1) 

### k=l 

# =Bl(Tj) 

## X Qssk=l(Tj)
whereXk=l Bl(Ti) 

### = 

### Load f;>ct.,r. Building cooling load (Btu/hr) at temperature (Tj)**fro~** 

### section 5.1.3 Qssk=l(Tj)= Steady-state coolina capacity (Btu/hr) at temperatures (Tj) from section 5.1.3. I

### CAS-RM-79-102 COMMENT 01

Federal Register / Vol. 44. No. 77 

### I Thursday. April 19. 1979 

### I Proposed Rules 23485

(2) 

## 'llliJ N 

### where

(3)**E~T**j)



### where

PlFk=l ,t=1 X Qsst.' (TI) y nj 

## r:

ratio of total cooling (Stll) in temoerature bin to the number of temperature bin hr·lrs.

is the fractiona1 

### number of hours in temoel'2tur" bin j 

### from 6.1.2



### ratio of Energy usage (I',att-hr) in temperature rin ; t.o 

### tr"**"I\~h~~ ~<** **t"'~~~Y'" t"Y'~**  H 

### n hours.

Where Co the degradation coefficient as described in section 2.1.3 or as calculated above in equation (1)
5.1.3.2 Hhen a unit must alternate between hi"h \1:=2) 

### and low (k=l) compressor speeds to satisfy the building coolinq load at 

### a temperature T5, evaluate the following equati0rs:

(l) 

### Xk=l 

### Q SS

### k=2(Tj) = 

## BL (Tj) Ossk=2(Tj)

- 05s

### k =1(Tj)


### (2) X k

=2 = 

### 1

_ Xk=l

(3) Q 

### (Tj) N



### (4) E(Tj) N 

### [Xk=' X

### 0ssk ='(Tj}

+ 

### Xk"2 X n 

### k=2(T. '1

. "\Iss 'l

...



### XE k=2(T'\

. 55 "

+ 

### X k

=2 XE s-

s -r.=2(TJ .)] 

### Xn· 

# rl 5.1.3.3**~Ihen** 

### a unit must cycle ('n a!'d /'Iff 

### at hiqh compl'essor speed (k=2) in order to satisfy the building coolinq load at a temperature Tj, evaluate the equations orovided in section 5.1.3.1 replacinq (k=l) data with the (k=?) 

### data.
5.1.3.4 When a unit operates continuously at hioh compressor speed.(k=2) at an outdoor temperature Tj evaluate the following equatlons:

. (1) 

### Q(Tj) "Q 

### k=2(T')**X~** "1[- 

### ss J N 

### (2) E(Tj) 

## = E ssk=2(Tj) X 

### OJ N i-C


### 5.1.3.5 Calculate the SEER in P.tU'S/V'iltt-'Y'. !Isinl1 t"e values for the terms

and

as determined at each temperatw'e bin according to the applicable conditions described in sections 5.1.3.1 throunh 5.1.3.4 as follows: 8 

# L**Q\~j)** SEER j=l 8 E(Tj) 

# L j=l N



### 5.1.4 Method for calculating a SEER for units with two speed compressor, two compressor or cylinder unloading capable of varying the sensible to total caoacity 

### (SIT) ratio. Multi-speed compressor and two-speed compressor units capable of varying the sensih1e to total capacity ratio (SIT) 

### shall have the seasonal energy efficiency ratio determined as r.escribed in section 5.1.3. For such units. the mode of ooeration selected to determine the steady-state capacjties Qssk(95), Ossk(82), Essk(95), E

ssk(82), and power inputs at each compressor speed k=l, k=2, for tests A and B is outlined in section 

### 2.10

### CAS~RM-79-102 

### COMMENT 01

23486 Federal Register /Vol. 44. No. 77 / Thursday, April 19. 1979

### I Proposed Rules

5.2 Calculation of Heat 1.ng Seasonal Performance
Factors (HSPF) for Air-Sou=ce Units.

The testing data and results required for these calculations shall include the following:

(i) Heating capacities (Btu/hr) from the indoor air enthalpy method for the High Temperature Tests, and
the total heating done (Btu's) for the cyclic
and frost accumulation tests

Q ss (47) or Q ss (62)

Q ss (17) Q cyc (47) Q DEF (35) 

# ---

Hi) Electrical power input to all components (watts)
for the steady state tests, and the electrical

usage (watt-hours) for the cyclic and frost
accumulation tests

E 55 (47) or E ss (62)

E ss (17)
E cyc (47)
E DEF (35) 

### .....,. (H

(iv) :cor air flow rate-{SCF:n an? external resistance

to indoor air flm

... (inches of ·.rater)

Air temperature (oF)

Outdoor dry bulb
Outdoor wet bulb or dew point
Indoor dry bulb and
Indoor wet bulb

(v) Data as specified in Table 

### II of 

### ASHRAE
Standard 37-69

Where the heating caoacities 0ss(47), 0ss(62) and Qss(17) and the indoor air'flow rate are calculated using
the equations specified in section 3.8.1 and 7.4 of ASHPAE
standard 37-69. The total heating done, 0cyc(47) and QDEF(35) are calculated using the eauations below.
Units not havincr an indoor fan as part of the model tested
shall add 1250 Btu/hr per 1,000 SCFM**o~** indoor air handled to
the measured capacity to obtain the total heating**ca~acity,**



# . 

# . Qss(17), Qss(47) or Qss(62), and add 365 watts oer 1,000
SCFM of indoor air handled to the**m~asured** power to obtain
the total power input, Ess (17), Ess (47), or ES5 (62), to the

unit.
The coefficients of performance (COP) for the High Temperature Tests COPss (62) or COP SS (47) , and Low Temperature

### CAS-RM-79-102 COMMENT 01

Fooeral lRegister 

### ! Vo!' 44. No. 77 

### I Thursday. April 19. 1979 / ProposedRules

-

Test, COPss (l7), are calculated as the ratio of the heating capacity in Btu/hr to the product of 3.413 and**~~e** power inputs to 

### the indoor 

### fan in watts and the power inputs to
the remaining equipment oomponents (including all controls)
in watts.
Por units which do not have indoor air circulating fans
furnished as part of the model shall adjust their total heating
done (Qcyc(47) and energy used £c'1c(471 in one comolete cycle for the effect of circulating indoor air equioment

pmver. For unit£! tested withol,lt an indoor fan as part of
the model, Qcyc(47) shall be increased by a**~uantity** of heat equal to the product of 1250 Etu/hr per 1,Ol)O SCFf1, the lengt:.
of the on-period of the test cycle in hours, and the flow

rate of indoor air circulated in units of 1,000 SCFM. The**tot~l** energy usage, E cyc (47), shall be the sum of the energy
usage required for air circulation during the test cycle and
the energy used by the remaining equipment components (including all controls) during the test cycle. Units not having

an indoor fan as part of the model tested, shall set the

energy recruired =or indoor air circulation equal to the quanti.ty given by the oroduct of 365 watts oer 1000 SC!"" , the length of the on-Deriod of the test c:'c1e in 'lours, and
the rate or indoor air circulatedl:: unit3 of 1000**SC!,,~i.** 'C'he cyclic coefficient of performance, COPcyc (47) is
calculate.a as the ratio**o~** the total heating done (Ocyc (47),
in Btu's to the product of 3.413 Btu/watt-hour and Lhe total

energy usage (Ecyc (47» in watt hours. The net heating capaCity, QDEP(35) (Btu/hrJ, is the t()tal

net heating done over the test period (including any credit
for the indoor fan heat) divided by the total length of the

test period, in hours. For units with "demand defrost control system", the net heating capacity, QDEP(35), shall be multiplied 

### by an enhancement factor of 

### 1,05 to compensate for improved performance not measured in the Prost Accunulation
Test. For units tested without indoor fans, the vahle
determined for QDEF(3Sl below shall be increased by a quantity of heat equal to the product of 1250 Btu/hr per 1000**SCF~\,** the length of time in hours during the Frost Accl,lmulation Test that there was indoor air circ'.llating, and
the average flow rate, of indoor air ci::cculated in units of
1000 SCFM.
The total energy usage, E m::F (351 shall be t.;';!? sum of
the energy. usage required for indoor-air circulation during
the test period and the energy used by the remaining eq-ui?1l'en'C components during the -test period, t'nits not having an
indoor fan as part of the model tested, shall set**~he** energy required for indoor air circulat:ion equal to the quantity given by the product of 365 watts per 1000 SCI''''. the length
of time in hours during the**~rost Acc~mulaticn**  Test that
there was indoor air circula.ting, and the average f10'\;, rate

6f indoor air circulated in units of 1000**SCF~,**

### CAS-RM-79-102 COMMENT 01

, '23488 Federal Register 

## I Vol. 44, No. 77 

### I Thursday. Apn119. 1979 

### I Proposed Rules**:~ng:h** 

### of che :esc period. in hours.**~~e ac:~al**  

### heating cone**c~ring** 

### the Cyclic Test,

- .- s.'nall be**deter~inee** 

### using the followino, 

### ea.uatior.: -=1':.

.. 

# I', '1)

where



## v ,.. the flow rate during the**on-~eriod**



### Cpa

.. calculated in accordance with section ;,4 

### of ASHRAE Standard 37-69 

### in**CF~ S~ecifit**  

### heat at 

### cor.stant Dressure of air- 'Iater Mixture per pound of dry air, (BtullboO!') , 

### " Specific volume of 

### air-vlater l'Iixture at the saMe dry-tulb temoerature. huric1ty ratiO, and pressure used in t"e :eter-ination of the indoor air flew rate (ft3 /lb). Hum;dity 

### ratio (1 b/lbl.


### and 

### r (hr-OF), which is described by tre equation:

where 

# f (time indoor fan off) f'" 

### [-:32(t;

- "'"l(t; )dt (time indoor fan on)

Tal (t) 

### " Dry-bulb terrperature of air 

### enterir9 tre indoor coil (OF) at time (t),
Drv-bulb terrperature of air leavino the indoor coil (OF) at til"e (t).

The net heating, QOEF (35) 

### in Btu's done during the

test period shall be determined using the following equationi (2)



### where 

# v s 

### the average, of the air flow rate calculated

at four or more time intervals throughout
the heating phase of ·the test using the equation in section 7.4 of ASHRAE Standard
17-69**Specifi~** 

### heat at constant pressure of airwater mlxture per pound of dry air (Stullb-oF) • ' Specific volume of air-water rnixtllre ,t the same dry-bul b**tem'ler~turp,** 

### hlJm;rli ty ratio, and pressure used in ·the determination of the indoor air flo., rate (ft3/lb), Wn % 

### Humidity ratio (lb/lb).
and 

### r (hr._oF), which is 

### described by the equat 

### ion

wherer 

# "'f(time indoor fan off) (time indoor fan on)

I.· 

### Dry-bulb temperature of air entering the indoor coil (OF) at time (t), Dry-bulb temperature of air leavinq the indoor coil (OF) at time (t),

-

### CAS-RM-79-102 COMMENT 01

Federal Register 

### I Vol. 44. No. 77 

### I Thursday, April 19. 1979 

### I Proposed Rules 23489

(3)**~yc1ic** degradation coefficient shall be calculated wheI"e

where

### as [01101"5,

1- COPcYC(47) COPss (47)


### HLF



### c**~** the cyclic degradation coefficient rounee

D to the 

### nearest ,01 COPcyc (47) as defined abo'"e
COPss (47) as defined above
HLF is the heating load factor calculated as follows; as defined above

OS5(47) as defined. above

T**~** Duration of time (hours) for one complete cycle consisting of one compressor "on"
time 

### and oue compressor "off" time,

5.2,1 calculation of the heating seasonal performance
factor (HSPF) far**air~saurce** heat pumps with single speed compressors,

For each climatic region listed in section 6.2.4, and
for design heating reqUirements equal to both the standardized
minimum and maximum de$ign hea'.:ing requirements defined below,
calculate the 

### HSPP defined as:

HSPf w
----------__________**4-~**______ d_

______________________ ___

where [ = fl, CL413) Ji;, .....J.. N RHCfJ

## )1

:l 

# J

j 1,2,3, ---, It corresponds to the jth temperature
bin
total number of non-zero temperature bins in
the climatic region

### CAS-RM-79-102 COMMENT 01

23490 Federal Register 

### I Vol. 44, No. 77 

### I Thursday, April 19. 1979 

### I Proposed Rules

Tj 

# = (67

- 5jl is the representative temperature
fof the jth bin,'(OF) I j 

## = indicated the quantity following the symbol
is to be summed over all temparature bins

ru!(Tjl supplementary resistance heat term,.**~t**

3.413-1'1-- temperature Tj required in those caseswhere the heat pump automatically turns
off (Tj<Toffl or when it is needed to meet,the balance of the building heating requirements. (kW)**~** = is the number of hours in the jth temperature 1'1 bin divided by 

# N=I nj and is referred,to as the "fractional hours in jth temperature bin"
is a conversion factor ,.,hich converts

watt hours to Btu building load at temperature Tj! (Btu/hrl
heat pump low temperature cut-out factor "X(Tj) '" heat pump heating load factor PLF(X) heat pump part load factot

are defined by the following equations:

( 65

- Tj 

# )(C) (DHRl

65

- TOO and ,,'here (el

- 0.77 is a correction factor which tends

to improve the agreement l"etween calculated
and measured building loads
(DHR) the minimum and maximum design heating

where

where requirement which the heat pump is likely.

to encounter when installed in a residence,
rounded off to the nearest standardized
OHR in section 6.26 in kBtu/hr

(c5-Ton) •

60**~** for regions ., II, :::, IV, ana \"1
f or region \1

(65-T ) , • 00 

# l 2C:SS (47) --6-0-- • for regions
2.2Qss(47), for region V

Qss (47) is the heat pump capacity measured ,during the High Temperature
Test @ 47°F
is the outdoor design temperature given in, section 6.2.4 I,. I1**~** II!, IV t**a~.d** Vl

### CAS-RM-79-102 COMMENT 01
Federal Register 

### I Vol. 44. No. 77 

### I Thursday. April 19. 1979 

### I Proposed Rules 23491

0(1j ) 

# .

X(T

### J) 

# I

I'L.(X) •

RH(T. ) 

### --L.

N



### where

TOFF

.. 0 1j 

### .! 10FF or Q(T

### J

## >

< 1 (3.413)(ECT

### J

## »
1 1 T

### o' F < Tj 

### .! TON and Q(T

### J) 1. 1 

### '2 O.413)(i(Tj 

# »

1 Tj > TON and Q(T

## J> 1. 1 (3.413) (t(Tj ) BL(T

### J) Q(Tj ) 

### 1. BL(Tj ) Q(Tj )

1 Q(Tj) 

### .! BL(Tj )

[SL(T

### J)


# - iHT

### J) XCT

## J) 6(T

### J) 

# ] i:1 3.413



### the outdoor temperature that the compressor is automatically shut off at' (If 

### no such temperature exists, TJ 

### is always greater
than TOFF and TON'}
TON • the outdoor temperature that the compressor is automatically turned on (if applicable)
if designed for low temperature automatic
shut-off.
C 

# = deg'radation factor determined described in

D 

### section 

### 5.2 and 

### 2.2.1 In using the above equation to calculate HSPF, the heat
pump capacity in Btu/hr, Q, 

### and the cower in watts, E, shall be obtained as follows:

, (ESS (47)

- E 

### ss (17»{!j

- 17) ESS(17) 

### + 30 ' T j 

### 1.

### ~5'F or T j 

### .! 17-:



### where Oss(47) and Ess(47) and QOEF(35) and Ess (47) and



# . Qss(17) and Ess (17) are the capacities (in Btu/hr) and powers (in watts) measured during the High Temoerature Test, the
Frost Accumulation test, and the Low Temperature 7est, respectively,

\

### ,CAS-RM-79-102 COMMENT 01

23492 Federal Register 

### I Vol. 44. No. 77 

### I Thursday. April 19. 1979 

### I Proposed J

Once the maximum and minimum HSPF and operating cost values
have been obtained for each region. the HSPF and operating

cost shall be determined for each standardized design heating requirement (see section 6.2.6) between the maximum and
minimum design heating requirements by means of interpolation.

5.2.2 Calculation of the heating seasonal**performan~e** factor (RSPF) for air source heat pumps with a two-speed compressor. two compressors. or cylinder unloading.

For each climatic region listed in section 6.2.4.
and for design heating requirements equal to both the
standardized minimum and maximum design heating requirements
defined below, calculate the HSPF defined as:

HSPF

[ .. !CTj)

.. RHCTj )] (3 4' 3)

.. +..

.

•• jill II

where



# .. as defined in 5.2.1 j

### ~ as defined in S.2.1

N 3.413 as defined in S.2.1

T" as defined in S.2.1 ,j BLITj) is the buildinq load at temperature Tj' in
Btu/hr. calculated by:

where

(e) R 0.77 is a correction factor which tend.

(ORR)

where to improve the agreement between
calculated and measured building loads

the minimum and maximum design heating requirement which the heat pump is likely

to encounter when installed in a residence,
rounded off to the nearest standardized
OHR in section 6.2.6 in Btu's per hour



### Q (k-Z)C'.7) 

### (65-ToO)**(~in~um desi~n**  heating**~equirement)** \ 5S 60' for regions I. 

### n. II!.

_ tv, and 'l!

• (ksZ) Q SS (47), for region V

.and

(maximum design heating requirement) -\ • k-2 (65-TOD) 20SS (47)--6-0-- • for regions I. II. III, 1'1, and VI

. K*2**2'~'QSS** (47) fo1' region V

### CAS-RM-79-102 COMMENT 01

Federal Register 

### I Vol. 44, No. 77 

### I Thursday, April 19, 1979 /Proposed Rilles 23493

Qss (47) is the heat pump capacitj' measured during the hiqh temperature performance

test at 47or, with the unit operating

at the high compressor**s~eed** or with
both compressors i.n operation. in
otu/hr is the outdoor design**ta~pera~ure** given in section**6.~.4** in degrees of
Note: the superscript (k"'l) and**(k~2)** refer**~.O** the heat

pump operating at. low speed 01: sin91e cpmpressor**op~ration** and high speed or**t~o co~pressor**  operation**respectivel~.**
is the heat pum?**elec~ric~l** energy tlsage in the**~~ t,~mperature** **bi~** divided by the totaL**nurn~er 0~**  bin hours and is
evaluated according to**~he** four**p0ssibl~**

cases of heat ?um? operation**de~oted** belOW in watts

RS (Tj 1 as defined in 5.2.1 and is evaluated 

### --N-- according to the four possible :ases of
heat pump operation denoted below. (in watts) cnits operating at low conpresso; speed or with a sinAte compressor, i.e.,
k,l, for which the building heating load, BL(Tj } 1s less than or equal to
the heating eapaci'y. Qk=l(Tj ). oL(tj )**~ Qk~l(Tj)** 

RH(T.) ---L

:l

6' (1j) 

# (



# .t E:C'l(Tj } xk:lcrj ) S'(Tj ?**?LFk~l**

0 Tj 

### .!. Ton 1**<Tj~TON** 

### 2 Tor:
1 T j > TON

### CAS-RM-79-102 COMMENT 01

23494 Federal Register 

### I .vol. 44, No. 77 

### I Thursday, April 19, 1979 

### I Proposed Rules

Units alternating**bet~een** high speed or**t~o co~pressor**  opera,ccn**(k~2)** and low speed or single compressor operation (k-1) to satisfy the building heating load at temperature T j 'k-l( .k=2( ) Q Tj ) < BL (Tj) < Q Tj

n. 

# -+ BL(Tj)[1

- 6' (Tj)

### J 3.413



# \0 T

. .: Ton- J
:'(T .) = t TOfF < T. ::**To~;** J 

### Z J

T

### J > TO'! CASE III Units cycling on and off at high compressor speed or cycling both

compressors on and off together (k-2) in order to satisfy the building heating load at temperature Tj . Qkal(Tj > < BL(Tj > < Qk.2(Tj )

tk"2(Tj) X k"'2(Tj)

## ~"(Tj)

# +

PLFk' Z

n. 

# -t BL(Tj)[l 3.413



# 1 0 T j**~** TOFf
"(T ) 

### " 1 T OFr < Tj**~ To~**  • j 

### '2

1. '**T()~** J

t:nits operating continuously at high compressor speed or ..,ith both

compressors in continuous operation (k-2) in order to satisfy the buildinl
heating load at temperature T j .

### CAS-RM-79-102 COMMENT 01

Federal Register' Vol. 44, No. 77 / Thursday, April 19, 1979 'Proposed Rules 23495

, .. (T.) J - 1.0
Qk-2 (T )**---~jL,,---** < 1 (j.413)(tkaZ (!j»
qk=2 (r.)

___**~JI-** __ > 1 (J.41J)(Ek=2(!.» J <?*2(! )

___ --,..J. j ..,-__ ! 1 (J .413) (Ek=Z (T j))

Where in each of the above cases

PLF heat pump heating load factor
heat pump part load factor (not required for cases II and III
heat pump low temperature cut-out
factor

as defined in 5.2.1

as defined in 5.2.1

the part load degradation factor described
in section 2.2.1 and 5.2 for the unit cycling at high compressor Speed or with
both compressors simultaneously cycling

(if applicable). .k-1 Q Crj) •**~k=-2** Q (!j)=

.k-2(T ) E j 

# r 

# 1 the part load degradation factor
described in section 2.2.1 and 5.2
for the unit cycling at low compressor speed or with the single compressor that normally operates at low heating
loads.
('k-1 .k-l) 'k=1 Q

### ss (62)

- Q

### ss (47) (!j Q



### ss (47) + 15 - 47)

('k=1 • •k-1 ) 

## 6

k=1(17) °DEF(35) - Q 

### ss (t7) (T

### 1

- 17) .Jo 55 18**~.k.l** .k-1 ) ·,,-1 Q

### ss (47)
- Q 

### ss (17) (Tj - 17) Q



### ss (17) + 30
(.k=2 .k-2 )

. k-2 Q S5 (47) - Q 

### ss (17) (Tj - 17) Q



### ss (17) + )0

( •k-2 •k=2 )
•k=2**C)"~F** (35)

- 

## ''ss (17) (Tj - 17) Q



### ss (17) + -- 18

-
( .k=l .k-l) 'k-1 ESS (62)

- ESS (47) (Tj - 47) ESS (47) + ...::;:::.-----=-1=-5-

- .... -'----

( .k a l .k-1) 'k-1 E D

",,(35)

- EoS (17) ('j

- 17) E' (17) +**~.** __ -:"::-'::-_...1._--'--_ 55 18
( .k-1 .k-1) 

# l. k-1

## ._E~S5::......(_4_7 }_-_E..: S ::;S:.-{_17_>..!..._{!..,Jj_-_1_7l ESS (17) + 30

( .1<=2 .k=2) "k"2 ESS (47)

- ESS (17) (Tj - 17) E55 (17) + 30 !j !. 40°1'

17°F! Tj < 40°1'

T.

J < 17°F



## , Tj ! 45°F or 

### r

### J ! 17°1'

17°, < !j < 45·1'

T

j 2. 40·1'

17'F**~** !j < 40'1'

17°F < T j < 4S·F

### CAS-RM-79-102 COMMENT 01

23496 Federal

### R~ister 

### I Vol. 44. No. 77 

### I· Thursday, Aprii lB. 1979 

### I Pl'Oposeli.Rules



### Calculate the heating seasonal performance factors
and seasonal operating costs corresponding to the standardized
maximum and minimum design heating requirements for each of
the six regions specified in Section 6.2.5. When the
maximum and minimum HSPF's and operating cost values have
been obtained for each region, the HSPF, and operating cost shall be determined for each standardized design heating requirement (see section 6.2.6) between the maximum and
minimum design heating requirements of that particular unit by 

### means of interpolation.
5.3 Calculations of the Actual Representative Regional Annual Performance Factors**~cr** 

### Air
Source Central Air Conditioners (Heat Pumps)
l'ihich Provide Both Heating and Cooling.
5.3.1 Calculation of actual reaional annual**perfor~ance** 

### factors (APFA) for a ?articular location and
for each standardized**de~ign** 

### heating requirement.

(CLE

## u ) 

## (Qssk(95Fl 1 + 

### (HLH&' (ORR) (Cl (CLHA) U;ssk (95Fl) + 

### (HLHA ) (DflR) (e) 

### (CSPF) (!-{SPF)

tvhere
is the actual cooling load hours for
the particular location, determined
from the map in section 6.1.3 (Q

### ssk(95,)) is defined in 5.1 (OHR) is defined in 5.2.2 (el 

### is defined in 5.2.2 where(HLHA) is the**actu~l** 

### heating load hours for
the particular location dete"rinined
from

.. the map in section 6,**~.** 

### 5

I 

### (CSPF) is the cooling seasonal performance
factor as determined in section 5.1 

### (HSPF)" is the heating seasonal performance
factors as determined in section 5.2
for each standardized design heating requirement within the particular
location's region or f?r the actual design heating requirement if known.

the particular location's region is determined from
the map in section 6.2.5 and, the standardized design heating requirements within the region are determined
in sections 5.2 and 6.2.6
5.3.2 Calculation of representative regional annual

(APFR ) performance factors (APFRl for each region

and fer each standardized design heating requirement

(CLHRl (Qssk( 95Fl 1 +**~HLHRl** 

### (OHR) (Cl
(CLHRl (Csl(951"» + 

### (HLHR) (DHR) (-C ) 

### CSPF HSPF Qssk (95F) ) is defined in 5.1 (OHR) is defined in 5.2.2 

### (Cl is defined in 5.2.2

### CAS-RM-79-102 COMMENT 01

Federal Register '/ Vol. 44, No. 77 / Thursday, April 19, 1979 / Proposed Rules 23497



### where

(CLHR ) is the representative cooling load hours
for each heating load hours region, as determined in section 6.3. 

### (HLHR) 

### is the representative heating load hours
for each region as determined in section 6.2.5 

### (CSPF) is the cooling seasonal performance factor

as determined in section 5.1 

### (HSPF) is the heating seasonal performance tactor

as determined in section 5.2 

### for each region
and for each standardized design healing requirement within each region.

where

the regions are listed in section 6.2.5 and, the
standardized design heating requirements within the regions are determined in sections 5.2 and 6.2.6 5.4 Calculations of cooling Seasonal Performance Factor
for Water Source units Which Provide Both Heating and Cooling. The cooling seasonal performance factor (CSPF)
for water-source heat pumps shall be calculated from the following equation:

CSPFj = 

### (Tj

- 

### TF) 

### COPE

- COPp) + 

### COPp (Tf;

- Tp) j


### Nhere Tj 

### =

Tp 

### =

Where any location from 6.4 

### of this Appendix ground water temperature of a given location in (OF) from 6.3 

### of this Appendix or a known design inlet water temperature between Soop and 900 

### F.


### the inlet water temperature (OF) 

### as described in test E 

### from 3.4.1 

### and 3.4.3 

### of this appendix
the inlet water temperature (OF) 

### as described in test F 

### ,from 3.4.1



### is the coefficient of performance from test E 

### detailed in sections 2.4, 3.4, 

### and**4~4** 

### of this Appendix' '
is the steady state cooling capacity (Btu/hr) obtained from test E 

### described above
is the electric input (watts) obtained from test E 

### described above, which shall include a factor of 60 

### watts per 12,000 

### Btu/hr of capacity measured in test p 

### detailed in section 2.4, 3.4, 

### and 4.4 

### of this Appendix to account for pump usage required to move the water through the heat exchanger (3.413) 

### is the conversion factor for Btu's per watthour

### CAS-RM-79-102 COMMENT 01

23496' Federal

## Register-I Vol. 44; No. 77

## .1 .Thursday, Api-i119; .1979 

## I· Proposed

# R~es

COPy

Where
COPF

(3.413)

## ~; ,(3.413)

is the coeffic,ient of performance from test B 

### detailed in sections 2.4, 3.4, and 4.4 of this Appendix is the steady state cooling capacity (Btu/hr) obtained from test F 

### described above
is the electrical input (watts) obtained from test B described above, which shall include a factor of 60 

### watts per 12,000 

### Btu/hr of capacity measured in test F described above, to account for pump usage required to move the water through the heat e'xchanger.
is the conversion factor for Btu's per watt-hour. 

### 5.5 calculation of Heating Seasonal Performance Factor :or water Source Units I-Ihlich Provide Both Heating and cooling. The heating seasonal performance factor (HSPF) for water-source heat pumps shall be calculated from the following equation: HSPFj

Nherej



### I,here any location from 6.4 of this Appendix



### = as described in 5.4 of this Appendix



### = the inlet water temperature (OF) as described in test G from 3.4.2 and 3.4.4 of this Appendix: the inlet water temperature (OF) as described in test H from 3.4.2 and 3.4.4 of this Appendix.


### £(; (3.413)



### is the coefficient of performance from test G detailed in section 2.4, 3.4, anc 4.4 of this Appendix. (3.413)

I,here

(3.413) 

### is the steady state heating capacity (Btulhr) obtained from test G as.described above.
is the electric input (watts) obtained from test G 

### as described above, which shall include a factor of 60 

### wattS per 12,000 

### Btu/hr of capacity measured in test E as 

### described above, to account for pump usage required to move the 

### water through the heat exchanger. '
is the conversion factor for Btu per watthour.

is the coefficient of performance from test H detailed in sections 2.4, 3.4, and 4.4 of this Appendix is the steady state heating ca?acity (Btu/hrl obtained from test G 

### as described above.
is 

### the electric input (watts) obtained from test 

### H as described above, which shall include
a factor of 60 

### watts per 12,000 

### Btu/hr of capacity measured in test G as described above, to account for pump usage required to move the water through the heat exchanger.
is the conversion factor for Btu per watthour. 5.6 Calculation of Annual Performance Factor For Water source Units Which Provide Both Heating and cooling. The annual performance factor (APF) for water-source heat pumps shall be calculated from the following equation:

APYj (HSPF;**~** 

### HLHj) + 

### (CSPFj 

### x CLRj) HLHj + CLHj

### CAS-RM-79-102 COMMENT 01

Federal Register 

### I Vol. 44. No. 77 

### I Thursday. April 19. 1979 

### I Proposed Rules .2349fJ



### Wherej 

### HSPFj

CSPFj .:



### = any location from 6.4 of this Appendix heating seasonal performance factor for any location j 

### as calculated in 5.5 of this Appendix heating seasonal performance factor for any location j 

### as calculated in 5.4 of this Appendix heating load hours for any location j 

### from 6.2.5 of this Appendix. cooling load 'hours for any location j 

### from 6.1.3 of this Appendix.23500



## 6.0 

## •

Federal Register 

## I Vol. 44. No. 77/ThursdaYi April 19. 1979 

## I Proposed Rules


## Reference f1ateria1

6.1 

## Cooling reference material

6.1.1 -Test operating and tcst condition" tolerancefOT cyclic dry-coi/ testa

Test Test condltlon

Readings. remarks (.pt"

..ting tole"'T)ce tolerance (variation

(lolal of a\'erage**ob~l)n'(:d** from range) spt>cified tt:st, conciltion)

Outdoor dry.rulb**ai~ temperatllr~**  l-'ahrr'nhcit:

Entering...•...,.........;

................, 2.0 0.5 Indoor drY.·btli!;**~.1:'**

tempcratcre,**F:.-~hr<:"'nheit:** l.'nt€ling

................................... Indoor**w~·t·Lulb** air

tr.mrwra:ur.e. l-\.nrenheit: 2.0 .5

Ezlter;r.g

................,................. ('j (I) Alter till' I:;t 30 s after
E!o\:t-rria.1**r·~.,i..,t**....r:-:,C to

aufivlJ.'.**lnrtH;~** wa!.t'T......• NOl.;".k**pr.:~.** tire**dr('~)~.** .05**p('r('i'!1~** 01**r(·:.::!~r:~** .,. ...... :.0**Elf'Cf!"I~;.! ~·{;lt;:.;::(':**  Ui;-:t.ts



## "'0 the tp)t. unit. t:1{'rc(.'nt.. 2.lI 

## ------------_._--------

'Shall at no timt' f'XC'N J lh::'d vatu? .,f t'nf; Wt·t

.. bulb**t~·mp.** r·t.! Il,r \l;hirh**rl·.<.tll~5** in**~** l.f**~_.I ",(b!"tif'\~.**  0!**C'n~l'!j·n~;\'~·** by Ti;f u)(ku"'r (.,!l**::~t** thp dry butb**t'·!npc~;\.tu:,'>":** {';'.].:!**.n~** l;;r thi:**::~.r** C)lt'rlllt! lhc indoor portIon of t.he unit.



## 6.1.2

. -iJi«ri'JI:fion offractional hours in tU;:}Jcrflil.1fe:**~'I~;S** /() (ll

.. •**i.~{!fifvr** c.llcl:lalion ofthe Si.·ER fo,- 2·spccl1 cor,prf's;wr and 2-**(·t.l1iLprC~:80T** lint's**---------.~.-** 

### - - 

## -- --------
!1.1H**t~.'rri· J~~.'~Jlt'S('fttf\·**  Fn;.,c.tion 01 Ilf'LJ.tt;:,(·**L1~":'** t';'ln·**tv~al len~1** 

I"<llor.'" per:nuro::- lIP H\lurr! (dl-grct's b\ll for**bir~** huurs f1;':rt'nheiO (dt>8

....r:.::S nJN Fi:lhrcntH·il)



## -

## -------------------------- Bin No.,J; 

# --.-- -----. -. 

## -- _.-.

## -.------ 

## -------

I........ C "" <,9 2 .........•...•.. "iiJ I.') 'j<j 3

...............'**~1:J** l'l

................". (," t,., c.'; 5

....,........... n':"lv 1:9

....... 6

...._........... 9l) to fi4

....... 7,

............... 95 to 1.19

....... C

................ Iv.) tv WL. .:! 7'j 82 t'; 92 9'/ 102 .214**.2~1** .216 .161 .104 .Oli:J .018 .004 

# •Alaska Canal lone Guam Hawaii Puerto Rico Samoa Virgin Island

- 

## o 6,000 6,600 2,300 6,000 6,600 6,000 

### (). 1. 

### 3

Cooling Load 

### CAS-RM-79-102 COMMENT 01

Federal Register 

### I Vol. 44, No. 77 

### I Thursday, April 19, 1979 

### I Proposed Rules**[)i~,trj** 

### bution of l\ctual Cooling Load IIours (UAll\'**'~hrouqhout** 

## the Unilp.d 

## States'

Hours 23501

### CAS-RM-79-102 COMMENT 01

Z3502

. Federal Register 

### I Vol. 44. No. 77 

### I Thursday. April'19. 1979 

### I Proposed Rules

6.2 ReaC1ng**Ref~renee** Material
6.2.1 Test operating and test cond1tion tolerance for

Steady-State High Temperature Test tat 47°F (8.3·C) or 62°F (16.70C)1 and Low Temperature Test tat 17°F (-8.3°C>1

Indoor dry-bulb. Entering Leaving
Indoor we e-bulb, Entering Leaving
Outdoor dry-bulb, Entering Leaving
Outdoor vee-bulb,



## ,Entering Leaving OF

OF

OF

OF

External resistance to**~ir** flow, inches of water
Electrical voltage, : Test Operating* Tolerance

2.0 2.0

l.0 1.0

2.0 2.0

l.0 l.0

.05
2.0 Test**Condition~~** Tolennce

0.5

O.S

0.3

•02

• Test Operating Tolerance is the maximum permissable variation of any**mea.ur~­** ment; When expressed as • percentage, the

....ximum a1 towable variation is the specified percencage of the average value•

•• Test Condition Tolerance i. the maximum**per~is.able** variation of the aver••e value of the measurement from the standard or desired test condition. 

# .. 6.2.2 Teat.. onerat1n& aw:L.teat-.cond4.e1cI:o- eole_M-ioT-**t~4tI.period** portion of. C-1'el.ic. "

..**rfol:1ll~nCl!. ~** 

Indoor dry-bulb, ·F Entering Leaving
Indoor vet-bulb, OF Entering Leaving
Outdoor dry-bulb, OF Entering Leaving
Outdoor vet-bulb, OF Entering Leaving
External relileance to air-flow, inches of

.. ater
Electrical voltage, : Test Operating**Toler.nees~** (App11e. after the ist 

### 30
aec. after c.ompr.ssor eeart-up)

2.0

1.0

2.0

2.0

.05
2.0 Test. Con.hnon Tolerancew';.

O.S

O.S

1.0

.02

• Test Operating Tolerance i. the maximum permi.sable variation of any measure- ment. When expresled as a percentage. the maximum allowable variation is the Ipacified percentage of the aver.ge value•

... Te.t Condition Tolerance is the maximum permi.lable variation of the average .alu. of the

.... ur

... nt from the atand.rd or desired telt condition•

### CAS-RM-79-102 COMMENT 01

Federal Register 

### J Vol. 44. No. 77 / Thurs'day. April 19. 1979 /Proposed Rules 23.503

6.2.3 Test oPp.t'3ting and test condition. tolerances fo[, frost acc"J.mU':'ati...,n**ta.S~5** t
'Ttlsting**Ofl~r.ting** Iolet"anceO ) Our1.ng He4tlng uurlog Delrost

Indoor dry-bulb, ., Entering Lelving
Indoor wet-bulb, ., Entering Leaving
Outdoor dry-bulb, ., Entering Leaving
outdoor dew-point I -r Entering Leaving
'E:x:tenal resistance to &ir-flow. inc:.hell of water 2.0

1.0

2.0

1.5



### .os

&lectrical .,oltage. % 2.0 4.0(3)

10.0 Test Condition Tolerance(2) (Heatlng POtt1on Otih)

O.S

1.0

0.7

.02

Test Operating Tolerance i. the maximum 'Pemiaaable variation of any measurement. When expre,sed a. a percentage, the uximum allowable variation is the specified percentage of the**~v1l!r.ge** value. Test Operating ToleTanee During Heating applies when the heat pump is LO the ht!ating mode, except :or the first S minutes after te1:'1Dioation of • defrost cycle. Teat OperatlDg Tolerance During 'Defrolt applies during. defrost cycle and. during the.first 5**~nu~es** after the tendnatioo of • defrost cycle when the heat ?W2IP l' operau.ng In the beatiag ...,de.
2 test Condition Tolerartee i. the. maximum**pet'rAiss.b~e** variation**o~ ~b.**  average value of the me••utemenc frOD the .tandard or**de'1re~** teet.**co~(h.t~ou.** "test Conditioa Tolerance applies only vben the beat pump 1.. operaclug UI. t.he beating ...,de.
lIat applicable during defrost if the indoor fan is off. 6.2.4 Ilistribution of fractional hours in temperature bins, heatirg load hours and outdoor design temp'erature for the different climatic regions 

# r Region I n III IV 

# r

Heating Load Hours, HLR 750 1250 1750 2250 I Outdoor DeSign**Temperatur~**

TOO for the region 37 27 17 5
Frac.tional ROUTS:

Bin # T1 (OF) j • 1 62 .291 .215 .153 .132 2 57 .239 .189 .142 .111 3 52 .194 .163 .138 .103 4 47 .129 .143 .137 .093 5 42 .081 .112 .135 .100 6 37 .041 .088 .U8 .109 7 32 .019 .056 .092 .126 8 27 .005 .024 .047 .087 9 22 .001 .OOS .021 .055 10 17 0 .002 .009 .036 11 12 0 0 .005 .026 12 7 0 0 .002 .013 13 2 0 0 .001 .006 14 -3 0 0 0 .002
15 -8 0 0 0 .001
16 -13 0 0 0 0 17 -18 0 0 0 

# I 0 18 -23 0 0 0 0

t- In Pacifie Coast Region V VI 

# ,
2150 2750' 

# 1

-10 30

I .106 .113 

# ,
, .092 .206 .086 .215 .076 .204 .078 .141 .087 .076 .102 .034 .094 .008


### , .074 .003 .055 0 .047 0 .038 0 .029 0 

# , .018 0
.010 0 i .005 a .002 0 

### , .001 0 I



## ----23504

b. ::.**~)**



## VI

3500 

### CAS-RM-79-102 COMMENT 01

Federal Register / Vol. 44. No. 77 

### I Thursday. April 19. 1979 

### I Proposed Rules

Ac tUed heat ing load hours (III (HUI 

## r) for the lInited States



### 2500 and regional heating 

### 103, irs



### Regional Heating Load Hours
Region HLlB

__


### 750 11 

### 1250 

### llr 1750

1\' 

### 1250 V 

### 2750 

### VI 27S0 This map IS reasonabty accurate lor most parts 01 the UllIted 

### Stales but IS necessan/y 

### hlUh/Y 

### ,generallled lind 

### consequently oot 100 accurate in mounlaUlOUS regIOns, piJlllcularly io 

## the Rockies 

## III

1500 

## II IV

Alaska 

### Hawaii and

- Territories 

### 3500 HLH 

# o HLH

# •

• r Federal Register 

## I Vol. 44. No. 77 / Thursday. April 19. 1979 

## I Pnoposed Rules



## 6.2.6 Standard Design Heating Requirements (Btu/hr)

5,000 25,000 50,000 90,000 10,000 30,000 60,000 100,000 15,000 35,000 70,000 110,000 20,000 40,000 80,000 130,000

6.3 Representative Cooling Load Hours (CLHR ) for Each Heating Load Hours Region

Region CLHR HLHR



## I 2400 750

II 

## 1800 1250


## III 1200 1750



## IV 800 2250



## V 400 2750


## VI 200 2750 23505

### CAS-RM-79-102 COMMENT 01

23506 Federal Register 

### I Vol. 44. No. 77 

### I Thursday. April 19. 1979 { Proposed Rules



## 6.4 Ground Water Temperature Map



## AVERAGE TElvjflEIlATURE OF 

## SHALLOW GROUND WATER IN O::=GIlEES FAHAENHErr