### h' 8 0 U L E /1, 

### Fi LIN G OJ

. i " (0 1\ i / 

# 1981' STA AR 

# for " UNITARY· AIR-CONDITIONING EQUIPMENT

### SECTION
Section 1. Purpose TABLE OF CONTENTS


### PAGE

Section 2. Scope

. Section 3. Definitions

. Section 4. Classification

. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. 2
Section 5. Testing and Rating Requirements " 2
Section 6. Performance Requirements
Section 7. Safety Requirements
Section 8. Conformance

. Appendix A



### FOREWORD



## This standard is prepared primarily for use in connection with, and is a part of, the ARI Unitary Air-Conditioner Certification Program. ARI, as copyright owner ofthe standard, reserves the right at all times to question any claims ofconformance and to testthe equipmentofany manufacturermaking such claims. It 

## is also understood that non-participants in the ARI Certification Program based on this standard shall have no right to use the ARI Certification Symbol, or any facsimile or reproduction thereof, on any of their equipment or literature pertaining to said equipment.

This standard supersedes ARI Standard 210-79 5


### 7
8
8

Price $6.50 Prmtecl in US.A 

### © COPYRIGHT" 1981, by Air-Conditioning and Refrigeration Institute

### __________________________ A RI STAN DA R D 210-81 

# UNITARY AIR-CONDITIONING EQUIPMENT

Section 1. Purpose


### 1.1 Purpose. The purpose of this standard is to establish, for unitary air-conditioning equipment: definitions and classification; requirements for testing and rating; specifications, literature and advertising requirements; performance requirements; safety requirements; and conformance conditions. 1.1.1 This standardis intendedfor the guidance of the industry, including manufacturers, distributors, installers, contractors, consumers and all levels of government. 

### 1.2 Review andAmendment. This standardis subject to review and amendment as the art of the industry advances. Section 2. Scope 

### 2.1 Scope. This standard applies to factory-made residential, commercial, and industrial air-conditioners or matched assemblies defined in 3.1. 

### 2.1.1 Energy Source. This standard applies only to electrically-driven, mechanical compression type systems.


### 2.2 Exclusions. This standard does not apply to the rating and testing ofindividual assemblies, such as condensing units or coils, for separate use. 2.2.1 This standard does not include standards for heating equipment or for the heating function of unitary air-conditioning equipment except for safety requirements. (See 7.3.) 2.2.2 This standard does not apply to unitary heat-operated air-conditioning equipment, to heat pumps, to packaged terminal air-conditioners, or to room air-conditioners. 2.2.3 This standard does not apply to unitary airconditioners as defined in ARI Standard 360, with capacities 135,000 Btuh [40 kW] and greater.
Section 3. Definitions


### 3.1 Unitary Air-Conditioner. A unitary air-conditioner consists of one or more factory-made assemblies which normally include an evaporator or cooling coil, a compressor and condenser combination, and may include a heating function as well. Where such equipment is provided in more than one assembly, the separated assemblies are to be designed to be used together, and the requirements of rating outlined in this standard are based upon the use ofmatched assemblies. 

### 3.1.1 Functions. The functions of unitary airconditioners, either alone or in combination with a heating plant, are to provide air-circulation, aircleaning, cooling with controlled temperature, and dehumidification, and may optionally include the function ofheating and possibly humidifying.


### 3.2 Published Rating. A statement of the assigned values of those performance characteristics, under stated rating conditions, by which a unit may be chosen tofit its application. Thesevalues apply to allunits oflike nominal capacity and type (identification) produced by the same manufacturer. As used herein, the term "published rating" includes the rating of all performance characteristics shown on the air-conditioner or published in specifications, advertising, or other literature controlled by the manufacturer, at stated rating conditions.


### 3.2.1 Stcindard Rating. A rating based on tests performed at Standard Rating Conditions.


### 3.2.2 Application Rating. A rating based on tests performed at application rating conditions (other than Standard Rating Conditions).


### 3.3 Rating Conditions. Any set ofoperating conditions under which a single level of performance results, and which causes only that level ofperformance to occur. 

### 3.3.1 Standard Rating Conditions. Rating conditions used as the basis of comparison of performance characteristics.


### 3.4 Energy Efficiency Ratio. A ratio calculatedby dividing the cooling capacity in Btuh by the power input in watts at any given set ofrating conditions, expressed in Btuh per watt [Btuh/watt].


### 3.4.1 Standard Energy Efficiency Ratio. A ratio calculated from the capacity and power input values obtained at Standard Rating Conditions.


### 3.5 SeasonalEnergy EfficiencyRatio (SEER). Seasonal Energy Efficiency Ratio means the total cooling of a central air-conditioner Btu's during its normal usage period for cooling (not to exceed 

### 12 months) divided by the total electric energy input in watt-hours during the
same period, as determined in Appendix A.


### 3.6 "Shall", "Should", "Recommended", or "ItIs Recommended". "Shall", "should", "recommended", or"it is recommended" shall be interpreted as follows:


### 3.6.1 Shall. Where "shall" or "shall not" is used for a provision specified, that provision is mandatory if compliance with the standard is claimed. 

### 3.6.2 Should, Recommended, or It Is Recol1l mended. "Should", "recommended" , or "it is 

### n",

### AR I STA NDA R 0 210-81

_



### Table 1-

### Classification of Unitary Air-Conditioners
Types of Unitary Air-Condilioners Designation ARI Type Heat Rejection Arrangement

Single Package "'SP-A Air 

# I FAN 

# I COMP 

# I
SP-E Evap Cond EVAP COND SP-W Water Refrigeration RCH-A Air 

# I COMP

# I

Chassis RCH-E Evap Cond j EVAP COND RCH-W Water

Year-Round SPY-A Air 

# I

FAN 

# I

Single SPY-E Evap Cond 

### COMP

# I Package SPY-W Water

### ~EAT YAP COND

Remote RC-A Air 

# mi3

Condenser RC-E Evap Cond AP 

### I COND 

### I RC-W Water

Year-Round RCY-A Air FAN

Remote RCY-E Evap Cond EVAP 

### I COND 

### I Condenser RCY-W Water HEAT COMP Condensing RCU-A-C Air 

### I EVAP 

### I 

# I COND 

# I

Unit Coil RCU-E-C Evap Cond COMP Alone RCU-W-C Water Condensing RCU-A-CB Air 

# I FAN 

# I 

# I COND 

# I

Unit Coil RCU-E-CB Evap Cond EVAP COMP and Blower RCU-W-CB Water

Year-Round RCUY-A-CB Air 

### r FAN 1

Condensing RCUY-E-CB Evap Cond 

### r EVAP 1 

# I COND 

# I
Unit and Blower RCUY-W-CB Water HEAT COMP

Extracted by permission from Table J. Chapter 42. 1979 ASHRAE Handbook.
A suffix of" -0" following any of the above classifications indicates equipment not intended for use with field-installed duct systems (See 5.1.3.7).



### ommended" is used to indicate provisions which
are not mandatory but which are desirable as good practice.

Section 4. Classification


### 4.1 Classification. Normally, unitary air-conditioners within the scope of this standard may be classified as shown in Table 1:

Section 5. Testing and Rating Requirements


### 5.1 Standard Ratings. Standard ratings shall be established at the Standard Rating Conditions specified in 5.1.3. All standard ratings shall be verified by tests conducted in accordance with the ASHRAE Standard 

### Methods ofTestingfor Rating Unitary Air-Conditioning andHeat Pump Equipment (American Society ofHeating, Refrigerating and Air-Conditioning Engineers, Inc. Standard 37-78), and with the test methods and procedures as described in this standard.

In addition, Seasonal Energy Efficiency Ratio (SEER) shall be determined for unitsrated less than 65,000 Btuh with air-cooled condensers and single-phase power
2 

### input in accordance with Appendix A. Otherequipment within the scope of this standard may have the SEER determined (as an application rating) in accordance with Appendix A, at the option ofthe manufacturer.
Standard Cooling Capacity shall be stated as total (sensible plus latent) cooling capacity. Power input shall be the total power input to the compressor(s) and fanes), plus controls and other items included as part of the model number(s).
Standard Ratings of units which do not have indoor air-circulating fans furnished as part of the model, i.e., refrigeration chassis units and condensing units with coil alone (See Table 1), shall be established by subtracting from the total cooling capacity 1250 Btuh/l000 cfm [0.172 Wper tis) 

### and by adding to the total powerinput 

### 365 watts/lOOO 

### dm {0.172 W per tis) 

### of indoor air handled. Standard Ratings of water-cooled units shall include a total allowance for cooling tower fan motor and circulating water pump motor power inputs to be added in the amount of 10 watts per 1000 Btuh cooling capacity [10 watts per 293.1 watts cooling capacity). Units equipped with desuperheater/water heaters shall be rated in accordance with ARI Standard 290.

### _________________________ AR I STAN DARD 210-81



### 5.1.1 Values of Standard Capacity Ratings. These ratings shall be expressed only in terms ofBtu per hour (Btuh) [watts] in multiples of: 

### 5.1.3.2 Seasonal Energy Efficiency Ratios. SEER's shall be determined at the temperature conditions specified in Appendix A.

"For units or portions thereof intended to be installed only indoors, this temperature may be reduced to 80 F [26.7"C] dry bulb. 

### 5.1.2 Values of StandardEnergy EfficiencyRatios and Seasonal Energy Efficiency Ratios. Standard ratios of energy efficiency, whenever published, shall be expressed in multiples of 0.05 Btuh/watt [cooling COP to 0.05].


### 5.1.3 StandardRating Conditions. The conditions of test for Standard Ratings shall include the following:


### 5.1.3.1 Standard Rating Temperatures. Standard Capacity Ratings and Standard Energy Efficiency Ratios shall bedetermined atthe following temperature conditions:

Item Conditions
Air temperature entering 80 F [26.7°C] indoor portion ofunit dry bulb 67 F [19.4°C] wet bulb
Air temperature 95F [3SOC] 

### surrounding unit dry bulb*


### For air-cooled units Air temperature entering 95 F [35°C] dry outdoor portion ofunit bulb (and 75 F [23.9°C] wet bulb when condensate is rejected to the air stream)



### For evaporatively-cooled units Air temperature entering 95 F [35°C]

outdoor portion ofunit dry bulb 75 F [23.9°C] wet bulb


### For water-cooled units Water temperature entering 85 F [29.4°C]

condenser Water temperature leaving 95F [35°C]

condenser Capacities (Btuh) [W] Less than 20,000[5,900] 20,000-37,800[5,900-11,000] 38,000-64,500[11,100-18,900] 65,000 and above [19,000] Multiples (Btuh) [W]

100[30] 200[60] 500[160] 1,000[300] 

### 5.1.3.3 Electrical Conditions. Recommended nameplate voltages are shown in Table 1 ofARI Standard 110 for 

### Air-Conditioning and Refrigerating EquipmentNameplate Voltages.
Standard Rating Tests shall be performed at the nameplate rated voltage and frequency.
For air-conditioners with dual nameplate voltage ratings, Standard Rating tests shall be performed at both voltages, or at the lower of the two voltages, ifonly a single Standard Rating is to be published.



### 5.1.3.4 Cooling Coil Air Quantity. All Standard Ratings shall be determined at a cooling coil air quantity, delivered against at least the minimum external resistance required by 5.1.3.7, as outlined below. All air quantities shall be expressed as dm [tis] 

### of Standard Air (density of 0.075 lb per Cll 

### ft) [1.2 kg/m3].



### a. Air-conditioners employing cooling coil fans with adjustable-speed drives shall be rated at the air quantity specified by the manufacturer in his Standard Ratings, not to exceed 37.5 dm per 1,000 Btuh !0.06 tis

### perwatt] ofrated cooling capacity, orat the air quantity ofwhich the drive is capable when operating against the external resistance specifiedin 5.1.3.7, whicheveris less.
b. For air-conditioners employing directconnected air-circulating fans, the cooling coil air quantity shall be as specified by the manufacturer in his Standard Ratings, not to exceed 37.5 dm per 1,000 Btuh [0.06 tis 

### per watt] of rated cooling capacity, or the air quantity produced by thefans when operatin.g against the external resistance specified in 5.1.3.7, whichever is less.

c. Air-conditioners whit:h do not incorporate
acoolingcoilfan, butarerated in combination with a device employing a fan shall be rated as described under a. or b. above, whichever applies. For air-conditioners of this class which are rated for general use to be applied to a variety of heating plants, the cooling coil air quantity shall be as specified by the manufacturer in his Standard Ratings, not to exceed 37.5 dm per 1,000 Btuh [0.06 tis 

### per watt] of rated cooling capacity or the air quantity obtained through the coil assembly when the
3

### A R 1STAND A R 0 210- 81 ._._.--.---.,,,,..-------------



# - Table 2- Minimum LOMVI n.1
Standard Cooling Rates

Thousands ofBtuh) [kwl (Inches ofWater) [Pal Up thru 28 Up thru 8.2 0.10 24.9 29 thru 42 8.5 thru 12.3 0.15 37.4 43 thru 70 12.6 thru 20.5 0.20 49.8 71 thru 105 20.8 thru 30.8 0.25 62.3 106 thru 134 31.1 thru 39.3 0.30 74.7



### 4 

### pressure drop across the cooling roil assembly and the recommended enclosures and attachment means is not greater than 0.30 inches ofwater [74.7 Pal, whichever is less. Cooling -coil air quantities as referred to herein apply to the air quantity experienced when the unit is cooling and dehumidifying under the Standard Rating Conditions, specified in this section. The air quantity determined under this test, except as altered by automatic controls or as noted in 6.4, 6.5 or 6.6 shall be employed in

. all other tests prescribed herein without regard

to the resulting external static pressure. 

### 5.1.3.5 CondenserAir Quantity. All Standard Ratings for air-cooled or evaporatively-cooled units shall be determined at the condenser air quantity specified by the manufacturer where the fan drive is adjustable; or, where the fan drive is direct-connected, they shall be determined at the condenser air quantity inherent in the air-conditionerwhen operated with all ofthe resistance elements associated with inletlouvres and any ductwork and attachments considered by the manufactureras normal installation practice. Once established, the condenser air circuit of the air-conditioner shall remain unchanged throughout all tests prescribed herein, except as altered by automatic controls.



### 5.1.3.6 Requirements for Separated Assemblies. All Standard Ratings for airconditionersin which the condenserorcondensing unit is separated from the cooling coil, as in Types RC, RCY, RCV and RCUY (shown in Section 4), shall be determined with at least 25 feet [7.62 m] ofinterconnection tubing on each line, ofthe size recommended by the manufacturer. Such air-conditioners in which the interconnectiontubingisfurnished as an integral part ofthe machine not recommended for cutting to length shallbetested withthe complete length of tubing furnished, or with 25 feet [7.62 m] of tubing, whichever is greater. At least 10 feet [3.05 m] of the interconnection tubing shall be exposed to the outside conditions, with the rest of the tubing exposed to the inside conditions. The line sizes, insulation, and details ofinstallation shall be in accordance with the manufacturer's published recommendations.


### 5.1.3.7 Minimum ExternalResistances. Where the conditioned air-moving equipment is supplied as part of the unitary air-conditioner, such equipment shall be designed to work against, and tested at notless than, the minimum external resistance shown in Table 

### 2when delivering the rated capacity and air quantity specified in 5.1.3.4 and 5.1.3.5. Indoor airmoving equipment not intended for use with field-installed duct systems shall be tested at 0 in. water [0 

### Pal external pressure.
In interpreting this requirement, itis understood that filters, heating coils, and other equipment recommended as part ofthe air-conditioner be in place and that the net external resistances specified above are available for the duct system.


### 5.2 Application Ratings. Ratings at conditions of temperature or air quantity other than those specified in 5.1.3, may be published as application ratings, and shall be based on data determined by the methods prescribed in 5.1.


### 5.3 Publication ofRatings. Wherever application ratings are published or printed, they shall include, or be accompanied by, the Standard Rating, clearly designated as such, including a statement ofthe conditions at which the ratings apply.



### 5.3.1 Capacity Designation. The capacity designation used in published specifications, literature

oradvertising, controlled by the manufacturer, for air-conditioners rated under this standard, are to be expressed only in Btuh [watts] at the Standard Rating Conditions specified in 5.1.3 and in the terms described in 5.1.1 and 5.1.2. Horsepower.

### _________________________ ARISTAN DARD 210-81



### tons, or other units shall not be used as capacity designations.



### 5.4 

### Tolerances. To comply with this standard, pub;- lished cooling capacity ratings, energy efficiency ratios, and/orseasonalenergyefficiencyratios shallbebasedon data obtained in accordance with the provisions of this section, and shall be suchthat anyproduction unit, when tested, will meet these ratingsexceptfor an allowance to
cover testing and manufacturing variations; the amount ofallowance to be minus 5 per cent.

Section 6. Performance Requirements


### 6.1 

### Performance Requirements. To comply with this standard, unitary air-conditioners shall be designed and produced in accordance with the provisions ofthis section in such a mannerthat any production unit will meet the requirements detailed herein.



### 6.2 

### Maximum Operating Conditions Test. * Unitary air-conditioners shall be designed and produced to pass the following maximum operating conditions test with a cooling coil air quantity as determined in 5.1.3.4. For multi-capacity units, this test shall be conducted with unit controls set for maximum capacity.



### 6.2.1 

### Temperature Conditions.
For all units Air temperature surrounding unit 115 F [46.10c] 

### dry bulb** Air temperature entering indoor portion of 80 F [26.7°C] dry bulb 67 F [19.4°C] wet bulb


### For water-cooled units Water temperature entering

condenser 90 F [32.2°C] Water temperature leaving

condenser , 100 F [37.8°C]

*This test will become effective on publication of this standard, at the manufacturer's option, but not laterthanJanuary 1, 1982. If the manufacturer does not elect the new test procedures, the requirements for this test are those shown in 6.2 ofARI Standard 210-79.

**For units or portions thereof intended to be installed only

indoors, this temperature may be reduced to 80 F [26.7°C] dry bulb. 

### Forair-cooled units Outside air temperature

..... 11'5 F [46.1

## °el dry bulb (and 75 F [23.9°C] wet bulb when condensateis rejected to the condenser air stream) at the standard condenser air quantity specified and stated by the. manufacturer



### For evaporativeiy-cooled units Outside air temperature 100 F [37.8°C] dry bulb 80 

### F [26.7°C]

wet bulb Make-up water temperature 90 F [32.2°C]


### 6.2.2 

### Voltages. The test shall be run at the Range A minimumutilizationvoltagefrom ARIStandard 110, Table 1, based upon the unit's nameplate rated voltage(s). This voltage shall be supplied at the unit's service connection and at rated frequency. 

### 6.2.3 

### Procedure. The air-conditioner shall be operated for one hour at the temperature conditions and voltage specified.


### 6.2.4 

### Requirements. The air-conditionershall operate

.continuously without interruption for any reason for one hour. 

### 6.2.4.1 Units with water-cooled condensers shall be capable of operation under these maximum conditions at a water-pressure drop not to exceed 15 psi [l03.4 kPa], measured
across the unit.



### 6.3 

### Voltage Tolerance Test. * Unitary air-conditioners shall be designed and produced to pass the following voltage tolerance test with a cooling coil air quantity as determined under 5.1.3.4.


### 6.3.1 

### Temperature Conditions. Temperature conditions shall be maintained as shown in 5.1.3.1.


### 6.3.2 

### Voltages.


### 6.3.2.1 Tests shall be run at the Range B minimum and maximum utilization voltages from ARI Standard 110, Table 1, based upon the unit's nameplate ratedvoltage(s). Thesevoltages shall be supplied at the unit's service connection and at rated frequency. A lower or a higher volta.ge shall be used, if listed on the nameplate.

5

### ARt STAN DAR 0 

### 210-81

_

6 6.3.2.2 The power supplied to the airconditioner shall be adjusted just prior to the shutdown period (See 6.3.3.2) sothatthe resulting voltage at the unit's service connection is 86 per 'Cent of nameplate rated voltage when the compressor is on locked rotor. For the purpose of this standard, the compressor nameplate locked-rotor amperes may be used to determine thisvoltage. The propervalue ofno-load voltage which will give the specified voltage at lockedrotor conditions should be determined prior to the test. The locked-rotor current value of any motor shall be measured as follows:

a. All hermetic compressor motors shall be tested as a compressor assembly.
b. The motor winding temperature shall not exceed 77 F [25°C] when the voltage is applied.

c. The current reading shall be taken within four seconds after the voltage is applied. If 

### the test is repeated, the motor winding shall be allowed to cool to 77 F [25°C] or lower before the current is reapplied.
d. The voltage at the unit service connection, at the time the current reading is taken, shall be the manufacturer's nameplate rated voltage.

e. The locked-rotor current shall be measured with an ammeter, with the rotor actually locked.
6.3.2.3 Within one minute after the airconditioner has resumed continuous operation (See 6.3.4.3), the voltage shall be restored to the values specified in 6.3.2.1.



### 6.3.3 Procedure.
6.3.3.1 The air-conditioner shall be operated for one hour at the temperature conditions and voltage(s) specified.
6.3.3.2 Allpowerto the air-conditionershall be cut offfor a period sufficient to cause the compressor to stop (not to exceed five seconds) and then restored.



### 6.3.4 Requirements.
6.3.4.1 During both entire tests, the airconditioner shall operate without failure ofany ofits parts.
6.3.4.2 The air-conditioner shall operate continuouslywithoutinterruptionforanyreasonfor the one hour period preceding the power interruption.
6.3.4.3 The unit shall resume continuous operation within two hours of restoration of power and shall then operate continuously for one half hour. Operation and resetting of safety devices prior to establishmentofcontinuous operationis permitted.


### 6.4 Low-Temperature Operation Test. Unitary airconditioners shall be designed and produced to pass the following low-temperature operation test when operatin,g with initial air quantities as**de~rmined** 

### in 5.1.3.4, 5.1.3.5 andwith controls and dampers setto produce the maximum tendency to frost or ice the evaporator, provided such settings are not contrary to the manufacturer's instructions to the user: 

### 6.4.1 Temperature Conditions.
For all units Air temperature entering

indoor portion ofunit 67 F [l9.4°C] dry bulb 57 F [13.9°C] wet bulb


### For water cooled units Water temperature leaving

condenser 70 F [21.1 °C]


### Forair-cooled and evaporativelycooled units Outside air temperature 67 F [l9.4°C] dry bulb 57 F 

### [13.9°C] wet bulb*


### 6.4.2 Procedure. Thetestshallbe continuouswith the unit on the cooling cycle, for not less than four hours afterestablishmentofthe specifiedtemperature conditions. The unit will be 

### permitted to start and stop under control of an automatic limit device, ifprovided.


### 6.4.3 Requirements.
6.4.3.1 During the entire test, the aircon?itionershall operate withoutdamage to the eqUipment.
6.4.3.2 During the entire test, the air quantity shall not drop more than 25 per-cent from that determined under the Standard Rating test.
6.4.3.3 During the test, and during the defrosting period afterthe completion ofthetest, all ice

'The wet-bulb temperature condition is not required when testing air-cooled condensers which do not evaporate condensate.

## _________________________ARI STANDAR 0 210-81



### or meltage must be caught and removed by the drain provisions.


### 6.5 Insulation Efficiency Test. Air-conditioners shall be designed and produced to pass the following insulation efficiency test when operating with air quantities as determinedin 5.1.3.4and5.1.3.5 with controls,fans, dampers, andgrilles settoproducethemaximumtendencyto sweat, provided such settings are not contrary to the manufacturer's instructions to the user: 

### 6.5.1 Temperature Conditions.
For water-cooled units Air temperature entering and surrounding indoor portion ofunit 80 F [26.7°C] dry bulb 75 F [23.9°C] wet bulb Water temperature

leaving condenser 80 F [26.7°C]



### For air-cooled and evaporativelycooled units Air temperature entering and surrounding indoor portion ofunit 80 F [26.7°C] dry bulb 75 F [23.9°C] wet bulb* Outside air temperature 80 F [26.7°C] dry bulb 75 F [23.9°C] wet bulb*


### 6.5.2 Procedure. After establishment of the specified temperature conditions, the unit shall be operated continuously for a period offour hours.


### 6.5.3 Requirements. During the test, no condensed water shall drop, run, or blow offfrom the unit casing.


### 6.6 Condensate Disposal Test. ** Air-conditioners which reject condensate to the condenser air shall be designed and produced to pass the following condensate disposal test when operating with air quantities as determined in 5.1.3.4 and 5.1.3.5 and with controls and dampers set to produce condensate at the maximum rate, provided such settings are not contrary to the manufacturer's instructions to the user:

'The wet-bulb temperature condition is not required when testing air-cooled condensers which do not evaporate condensate.

"This test may be run concurrently with the Insulation Efficiency Test (See 6.4). 

### 6.6.1 Temperature Conditions.
Air temperature entering and surrounding indoor portion ofunit 80 F [26.7°C] dry bulb 75 F [23.9°C] wet bulb Outside air temperature 80 F [26.7°C] dry bulb 75 F [23.9°C] wet bulb 

### 6.6.2 Procedure. After establishment of the specified temperature conditions, the airconditioner shall be started with its condensate collection pan filled to the overflowing point and shall be operated continuously for four hours after the condensate level has reached equilibrium.


### 6.6.3 Requirements. During the test, there shall be no dripping, running-off, or blowing-off of moisture from the unit casing.


### 6.7 Tolerances. The conditions for the tests outlined in 6.2, 6.3, 6.4, 6.5 and 6.6 are average values subject to tolerances of ±1.0 F [±0.56°C] for air wet-bulb and dry-bulb temperatures, ±0.5 F [±0.28°C] for water temperatures, and ± 1.0 per cent ofthe reading for voltages.

Section 7. Safety Requirements


### 7.1 Refrigerating System. It 

### is strongly recommended that the refrigerating system be designed, constructed, and assembled so as to be 

### in accordance with the latest edition ofthe ANSI!ASHRAE 15-1978 

### Safety Codefor MechanicalRefrigeration (American SocietyofHeating, Refrigerating and Air-Conditioning Engineers, Inc.).


### 7.2 Underwriters' Laboratories, Inc. It 

### is strongly recommended that unitary air-conditioners be designed. constructed, and assembled so as to meet the safety requirementsofULStandardfor

### AirConditioners, Central Cooling (Underwriters' Laboratories, Inc. Standard 465, July 1978).


### 7.3 Heating Functions. In addition to the foregoing requirements ofthis section, it is strongly recommended that air-conditioners incorporating agas-fired, oil-fired,
or electrical heating function be designed, constructed, and assembled so as to meet the applicable safety requirements ofone ofthe following standards:

a. Gas-fired: American National Standard for 

### GasFired Gravity and Forced Air Central Furnaces (American National Standards Institute Standard Z21.47-1978 or American National Standard for 

### Gas-FiredHeavy Duty ForcedAirHeaters (American National Standards Institute Standard Z21.53-1967).

7

### ARI STAN DAR 0 

### 210-81

_

b. Oil-Fired: UL Standardfor 

### Oil-Fired CentralFurnaces {Underwriters' Laboratories, Inc. Standard 727, October 1975) or ULStandard for 

### Oil-Fired Unit Heaters (Underwriters' Laboratories, Inc. Standard 731, October 1975).

c. Electrical: UL Standard for 

### Heat Pumps (Underwriters' Laboratories, Inc. Standard 559, March 1980). Section 8. Conformance

8.1 

### Conformance. Conformance with this standard shall not be claimed or implied for unitary airconditioners coming within the scope of this standard unless the unitary air-conditionersfor which such claims
are made meet all the performance, safety and rating requirements specified herein.

2. Testing Required

2.1 Testing required forairsource cooling only units with single speedcompressors. 

### two-speedcompret1llOrs, two compressors. or cylinderunloading. Two steady state wet coil tests required to be 

### performed. test A and test B. TestA is to be 

### conducted as an outdoor dry

### bulb temperature of95" F and test B at 82" 

### F. Test Cand 0 are optional tests to be 

### conducted when cyclic performance parameters are to be 

### measured in orderto determine the degradation coefficient, 

## en Test C is a steady state dry coil test conducted at an outdoor dry bulb temperature of82° F. Test 0 is 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, CD. 

### APPENDIX A 

## *Uniform Test Method for Measuring the Energy Consumption of Central Air-Conditioners AppendixM to SubpartB-UniformTest 1.12 

### "Demand-defrost control system" which 

### all indoorand outdoorconditions are Method forMeasuring the Energy 

### means a system which is designed to perform held constant and the unit is 

### in non-changing Consumption ofCentral Air

### Conditioners the defrost function on the outdoorcoil ofthe operating mode. 1. Definitions heat pump only when a predetermined 1.24 

### '"Temperaturebin" means a S" F degradation ofperformance is measured. increment overa dry-bulb temperature range 1.1 "Annual performance factor" 1.13 "Design heating requirement (m·m)" 

### of65" Fthrough 104" 

### Ffor the cooling cycle
means the total heltting and cooling is the amount ofheating required to maintain and -25" 

### F through 

### 64" Ffor the heating done by a heat pump in a particular a given indoortemperature at a particular cycle. region in one year divided by the total outdoor design temperature. 1.25 '"TIme-temperature defrost control electric power used in one year. 1.14 

### "Dry-coil test" means a test system" means a system which automatically

1.2 

### "ARI" means Air-Conditioning and conducted at a wet-bulb**tempera'l'r~** 

### and a provides the defrost function at a Refrigeration Institute. dry-bulb temperature su,h that moisture will 

### predetermined timeinterval whenever the

1.3 

### "ARI Standard 210-79" 

### means the test not condense on the evaporator coil ofthe outdoortemperature drops below a level standard published in 1979by the ARI and unit. where frosting will occur. titled "Standard for Unitary Air-Conditioning 1.15 

### "Heating seasonal performance 1.26 

### '"Testcondition tolerance" means the Equipment". factor (HSPF)" 

### means the total heating output maximum permissible variation ofthe

1.4 

### "ARI Standard 240-77" 

### means the test ofa heat pump during its normal annual average ofthe test observations from the standard published in 1977 

### by the ARI and usage period for heating divided by the total standard ordesired test condition as tilled "Standard for Air-Source Unitary Heat electric powerinput during the same period. provided in 6.1.1, 6.2.1. 6.2.2, 

### and 6.2.3 

### ofthis Pump Equipment". 1.16 

### "Heating load factor (HLF)" 

### means Appendix.

1.5 

### "ARI Standard 320-76" 

### means the test the ratio ofthe total heating done in a 1.27 

### '"Test operating tolerance" means the standard published in 1976

### by the ARI and complete cycle ofa specified time period. maximum permissible difference between the titled "Standard for Water-Source Heat consisting ofan "on" time "off' time, to the maximum and the minimum instrument Pumps". steady state heating done overthe same observation during a test as provided in 6.1.1,

1.6 

### "ASHRAE" means the American period at constant ambient conditions. 6.2.1, 6.2.2, 

### and 6.2.3 

### ofthis Appendix. Society ofHeating, Refrigeration and Air- 1.17 

### "Latent cooling" means the amount 1.28 

### "Wet-coil test" means a test ConditioningEngineers, Inc. ofcooling in Btu's necessary to remove water conducted at a wet-bulb temperature and a

1.7 

### "ASHRAE Standard 37-78" 

### means the vapor from the air

### passing overthe indoor dry-bulb temperature such that moisture will test standard published by ASHRAE in 1978 

### coil by condensation during a periodoftime. condense on the testunit evaporatorcoil. and titled "Methods ofTesting for Rating 1.18 "Part-load factor (PLF)" 

### means the Unitary Air-Conditioning and Heat Pump ratio ofthe cyclic energy efficiency ratio to Equipment." the steady-state energy efficiency ratio at

1.8 

### "Continuously recorded" means a identical ambient conditions. method ofrecording measurements in 1.19 

### "Seasonal energy efficiency ratio intervals no greaterthan 5 seconds. (SEER)" means the total cooling ofa central

1.9 

### "Cooling load factor (CLF)" 

### means the air conditionerin Btu's during its normal ratio ofthe total cooling done in a complete annual usage period for cooling divided by cycle ofa specified time period, consisting of the total electric powerinput in watt-hours
an "on" time and "off' time, to the steady- during the same period. state cooling done over the same period at 1.20 "Sensible cooling" means the amount constant ambient conditions. ofcooling inBtu's performed by a unit over a

1.10 

### "Cyclic Test" means a test where the period oftime, excluding latent cooling. indoor and outdoor conditions are held 1.21 "Single package unit" means any constant, but the unit is manually turned "on" central airconditionerin which all 

### the major and "off' for specific time periods to simulate assemblies are enclosed in one cabinet. part-load operation. 1.22 "Split system" means any central air

1.11 "Degradation coefficient (Cn )" means conditionerin which one ormore ofthe major the measure ofthe efficiency loss due to the assemblies are separate from the others. cycling ofthe unit. 1.23 

### "Steady-state test" means a test in

'Copied from Appendix M, pages 76707 thru 76723 Federal Register. Vol. 44, No. 249. Thursday. December 27. 1979. This Appendix M is subject to change by the U.S. Government. Only those portions of Appendix M pertaining to air-source cooling-only units are to be used.


### 8

### _________________________ARI STAN DAR 0 210-81

2.1.1 Testing required for units with single speedcompressors andsingle speed condenser fans. Test A and test B shall be performed according to the testprocedures outlined in 4.1 ofthis Appendix. In addition. the cyclic performance shall be evaluatedby 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 described in section 2.1.1 for single speed condensor fan units.



### 2.1.3 Testing requiredfor units with twospeedcompressors. two compressors. or cylinderunloading. The test requirements for two-speed compressorunits. two compressor units. orunits with cylinder unloading are the
same as described in 2.1.1 ofthis Appendix except that test A and testB shall be performed at each compressor speed or at each compressorcapacity.



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



### 2.2 Testing required forairsourceheating only units with single speedcompressors. two-speedcompressors. two compressors. or cylinderunloading. Fourtypes oftests are required to be performed: High Temperature. Cyclic. FrostAccumulation. and Low Temperature. In lieu ofconducting the Cyclic Test an assigned value of0.25 may be used for the degradation coefficient. CD.



### 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.



### 2.2.2 Testing required for units with twospeedcompressors. two

### compressors. or cylinderunloading. With the unit operating: at high compressors speed (two-speed compressor). with both compressors in operation (two-compressors). or at the maximum capacity (cylinderunloading); 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 at 47" F) is required, with the unit operating at the high compressor speed (twospeed compressor), with both compressors in operation (two compressors). or at the maximum capacity (cylinder unloading); 

### if the normal mode ofoperation requires cycling "on" and "off' ofthe compressor{s) at high speed or maximum 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 at 47° F. the High Temperature Test at 62° F, and the Cyclil; Test Additional tests. (Frost Accumulation Test and Low Temperature Test) are required, with the unit operating: 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 (cylinder unloading). if the unit's low speed, one compressor or low capacity performance at and below 40' F is needed to calculate its seasonal performance.



### 2.3 Testing requiredforairsource 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 required for watersource units whichprovide both heatingandcooling. (Reserved) 

### 3. Testing conditions

3.1 Testing conditionsforairsource cooling only units with single speed compressors. two-speedcompressors, two compressors orcylinderunloading. The test
room requirement and equipment installation procedures are the same as those specified in sections 11.1 and 11.2 ofASHRAE Standard 37-78. Units designed for both horizontal and vertical installation shall be tested in the orientation in which they are most frequently installed. All tests shall be performed at the normal residential voltage and frequency for which the equipment is designed (either 115
or230 volts and 60 hertz). the test installation shall be designed such that there will be no airflow through the cooling coil due to natural orforced convection while the indoor fan is "off'. This shall be accomplished by installing dampers upstream and downstream ofthe test unit to block the offperiod air flow. Values ofcapacity for rating purposes are to be rounded offto the nearest 100Btu! hour for capacities less than 20,000 Btu/hour; to the nearest 200 Btu/hour for capacities between 20,000 and 37,999 Btu/hour; and to the nearest 500 Btu/hourfor capacities between 38.000 and 64.999 Btu/hour.

The follOWing conditions listed inARI Standard 210.79 shall apply to all tests performed in Section 3.1 ofthis Appendix: 5.1.3.4 Cooling Coil Air Quantity. 5.1.3.6 Requirements for Separated Assemblies. 

### 3.1.1 Testing conditionsfor units with single speedcompressors andsingle speed condenser fans. 3.1.1.1 Steadystate wet-coilperformance tests (TestA and TestB). TestA and test B shall be performed with the air entering the indoor side ofthe unit having a dry-bulb temperature of80° F and a wet-bulb temperature of87° F. The dry-bulb temperature ofthe airentering the outdoor side ofthe unit shall be 95° F in testA and 82' Fin testB. The temperature ofthe air surrounding the outdoor side ofthe unit in each test shall be 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 t.'le unit shall be 80° F. For those units which reject condensate to the condenser, located in the outdoor side ofthe unit. the outdoor wetbulb temperature surrounding the outdoor side ofthe unit shall be 75° F in testA 

### and 65' Fin test B.



### 3.1.1.2 Steadystate dry coilperformance test(Test C)

### andcyclicdrycoilperformance test(TestD). Test C and test D shall be performed with the air entering the indoor side ofthe unit having a dry-bulb temperature of80° 

### F and a wet-bulb temperature which does not result in formation ofcondensate on the indoorcoil. (It is reco=ended that an indoorwet-bulb temperature of57° F orless be used.) The dry-bulb temperature ofthe air entering the outdoor portion ofthe 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 cycling the unit "on" and "off' by manual or automatic operation ofthe normal control**~t** ofthe unit. The unit shall cycle with mpressor "(m" for 6 minutes and "for24 minutes. The indoor fan shall also cyde "on" and "off', the duration ofthe indoorfan "on" and "off' periods being governed by the automatic controls which the manufacturernormally supplies with the unit. The results oftests C and D shall be used to calculate a degradation coefficient, CD by the procedures outlined in 5.1 ofthis Appendix.



### 3.1.2 Testing conditionsfor units with singlespeedcompressors andmultiple-speed condenserfans. The condenserfan speed to be used in testA shallbe that speed which normally occurs at an outdoor dry-bulb temperature of95° F, and for testB, the fan speed shall be that which normally occurs at
an outdoor dry-bulb temperature of82° F. If elected to be performed, tests C and D shall be conducted at the same condenserfan speed as in testB.



### 3.1.3 Testingconditionsfor units with two-speedcompressors. two compressors. or cyh'nderunloading. The condenser fan speed used in conducting testA at each compressor speed shallbe that which normally occurs at
an outdoordry-bulb temperature of95° F. For testB. the condenser fan speed at each compressor speed shallbe that which normally occurs at an outdoor dry-bulb temperature of82° 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 testB. 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


### 9

### AR I STAN DAR 0 210-81

_

the compressor operating athigh speed and at a condenserfan 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 of82· F shall be operating.

In lieu ofconducting tests C and D, an assigned value of0.25 may be used for the degradation coefficient, 

### Co. at each compressor speed. Ifthe assigned degradation coefficient is used for one compressor speed itmust also 

### be used for the othercompressor 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 cylinderunloading capable of varying the sensible to total(SIT) capacityratio. The mode ofoperation selected for controlling the SITratio in the performance oftest A and testB at each compressor speed shall be such that it does notresultin an operating configuration which is not typical ofa 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 testB 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 S/ T control mode as in test A when performed at the high compressor speed.

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



### 3.2 Testing conditionsforairsource heating onlyunits with single speed compressors. two-speedcompressors. two compressors, orcylinderunloading. The equipment undertest shall be installed according to the requirements ofSection 11.2 ofASHRAE Standard 37-78 and Section 5.1.4.5 ofARI Standard 240-77. Test chamber requirements are the same as given in Section 11.1 ofASHRAE Standard 37-78. Units designed for bothhorizontal and vertical installation shall be tested in the orientation in which they are most often installed. All tests shall be performed at the normal residential voltage and frequency for which the equipment is designed (either 115 or230 volts and 60 hertz). Values ofcapacity for rating purposes are to be rounded offto the nearest 100Btu/hourfor capacities less than 20.000 Btu/hour: to the nearest 200Btu/hour for capacities between 20,000 and 37.999

### Btul hour; and to the nearest 500Btulhourfor capacities between 38,000 and 84.999

### Btul hour.



### 10 3.2.1 Testing conditionsfor units with single speedcompressors.

3.2.1.1 High temperature testconditions. The High Temperature Test at47" F shall be conducted at an outdoor dry-bulb temperature of47· F and an outdoorwet-bulb temperature at 43· F. The High Temperature Test at 62· F shall be conducted at an outdoor dry-bulb temperature of82· F and an outdoor wet-bulb temperature of58.5· F. Forboth tests. the dry-bulb airtemperature entering and surrounding the indoorportion ofthe unit shall be 70· F and a maximum wet-bulb temperature of60· F. The duration ofthe tests shall be for a minimum of Ifs hour.



### 3.2.1.2 Cycling testconditions. The Cycling Test at 47· F shall be conducted at the same dry-bulb and wet-bulb temperature
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 compressorcycles "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 shall be designed such that there 

### will be no airflow through the indoor unit due to natural or forced convection while the indoorfan is "off." This shall be accomplished by installing dampers upstream and downstream ofthe test unit to block the offperiod airflow.



### 3.2.1.3 Frostaccumulation testconditions. The dry-bulb temperature and the resultant dew-point temperature ofthe airentering the outdoorportion ofthe unit shall

### be 35· F and 30· Frespectively. The indoordry-bulb temperature shall be 70· F and the maximum indoor wet-bulb temperature shall 

### be 60· F. The Frost Accumulation Test requires that the unit undergo a defrostpriorto 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 eitherthe heating or defrostportion ofthe test.



### 3.2.1.4 Lowtemperature testconditions. The LowTemperature Test shall 

### be conducted at a dry-bulb temperature entering the outdoorportion ofthe unit of17· F 

### and a wet-bulb temperature of15· F. The air entering the indoorportion ofthe unit shall have a dry-bulb temperature of70· F and a maximum wet-bulb temperature of60· F.



### 3.2.1.5 Additionaltesting conditions. All tests shall be conducted at the indoor-side air quantities specified in Sections 4.1.4.3 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 ofthis Appendix. 

### 5.4.4.4 Outdoor-SideAirQuantity; and 5.1.4.5 RequirementsforSeparated Assemblies. In all tests. the specified dry-bulb temperature entering the outdoorportion of the unit also applies to the air temperature surrounding the outdoorportion ofthe unit. Similarly. models where portions are intended to be installed indoors shall have the air temperature surrounding that portion ofthe unit the same as the indoor air temperature.



### 3.2.2 Testing conditionsfor units with two-speedcompressors. two compressors or cylinderunloading. The testing conditions for two-speed compressors. two compressors. or cylinderunloading 

### shall be the same as those for single speedunits as described in 3.2.1.



### 3.3 Testing conditionsfor airsource units whichprovideboth heating andcooling. The testing conditions for units 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 units whichprovide hoth heatiIlg andcooling. (Reserved)



### 4.0 Testingprocedures. Measure all electrical inputs as described in the procedures below. All electrical measurements during all "on" and "off' periods shall include auxiliary poweror energy (controls. transformers, crankcase heaters. etc.) delivered to the unit.



### 4.1 Testingproceduresfor airsource cooling only units with single speed compressors, two-speedcompressors, two compressors, orcylinderunloading. All steady-state wet- and dry-coil performance tests on single package units shall simultaneously employ the Air-Enthalpy Method (Section 3 ofASHRAE Standard 37- 78) on the indoor side and one other method consisting ofeither the Air-Enthalpy Method
or the CompressorCalibration Method '(Section 4 ofASHRAE Standard 37-78 on the outdoor side. All steady-state wet- and drycoil performance tests on split systems shall simultaneously employ the Air-Enthalpy Method or the CompressorCalibration Method on the indoor side and the AirEnthalpy Method. the Compressor CalibrationMethod or the Volatile RefrigerantFlow Method (Section 5 of ASHRAE Standard 37-78) 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 installed 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 5.1.3.4. 5.1.3.5, and 5.1.3.7 ofARI Standard 210.79.



### 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 37-78 and evaluated in accordance with the cooling-related requirements ofSection 12 ofthe ASHRAE

## _________________________ARI STAN DARD 210-81

Standard 37-78. 

### The testroom reconditioning apparatus and the equipmentunder test shall be operated until equilibrium conditions are attained.



### 4.1.1.2 Steady-state andcyclic dry-coil performance tests (Test CandTestD). The steady-state and cyclic dry-coil tests {C and D} shall be conducted as described belowin accordance with the conditions describedin sections 3.1.1.2, 3.1.2, 3.1.3, 3.1.4, 

### and 3.1.5 

### of this Appendix. The results shall be evaluated in accordance with the cooling related requirements ofSections 12.1.5, 12.1.6, 12.1.7, 

### ofASHRAE Standard 37.78. 

### The test room reconditioning apparatus and the equipment under test shall be operated until equilibrium conditions are attained, but not for less than
one hourbefore data for test C are recorded. For all equipment test methods including the CompressorCalibration Method. test C 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 37-78. 

### When the Air-EnL'lalpy 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 ofSection 3.6 

### ofASHRAE Standard 37-78 

### shall also apply. Immediately after test C is completed the test unit shall be manually cycled "off' and "on" using the time periods from 3.1.1 

### of this Appendix until steadily repeating ambient conditions are again achieved in both the indoor and outdoor test chambers, but for not less than 2complete "off'/"on" cycles. Without a breakin the cycling pattern, the unit shall berun 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 test 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 airmoving equipment on the condenser side shall cycle "on" and "off' when the compressor cycles "on" and "off'. The indoor airmoving equipment shall also cycle "off'
as governed by any automatic controls normally installed with the unit. This last requirement applies to units having an indoor fan time delay. Units not supplied with an indoor fan time delay shall have the indoor airmoving equipment cycle "on" and "off' as the compressor cycles "on" and "off,"



### 4.1.2 Testinstrumentation. The steadystate and cyclic performance tests shall have the same requirements pertaining to instrumentation and data as those specified in Section 10 andTable DofASHRAE Standard 37.78. 

### Forthe 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 of2.5 seconds or less. Response time in the time required for the instrumentation to obtain 63 percent ofthe final steady-state temperature difference when subjected to a step change in temperature difference of15° 

### F ormore. Electrical measurement devices (watt-hour meters) used during all 

### tests shallbe accurate to within ±0.5 percent ofindicated value.



### 4.1.3 Test tolerances. All steady-state wet-and dry-coil performance tests shall be performedwithin the applicable operating andtestcondition tolerances specified in Section 11.6 andTable 

## mofASHRAE Standard 37-78.

4.1.3.1 

### The indoor and outdoor average dry-bulb temperature for the cyclic dry coil testD shall both be within 1.00 

### F ofthe indoor and outdoor average dry bulb temperature for the steady-state dry coil test C, respectively.

4.1.3.2 

### The test condition and test operating tolerances for conducting testD are stated in 6.1.1 

### ofthis Appendix. Variation in the test conditions greater than the tolerances prescribed in 8.1.1 

### ofthis Appendix shall invalidate the test. It 

### is suggested that an 'electric resistance heaterhaving a heating capacity approximately equa'! to the sum of the cooling capacity and compressor and condenserfan powershould be installed in the outdoor testroom and cycled "off' and "on" as the unit cycles "on" and "off' respectively to improve control in the outdoor test room. Similarly, an electric resistance heater having a heating capacity approximately equal to the cooling capacity ofthe unit could be installed in the indoor test room. and cycled "on" and "off' as the test unit cycles "on" and "off' to improve indoorroom control.



### 4.2 Testingproceduresforairsource heating only units with single speed compressors, two-speedcompressors, two compressors. orcylinderunloading.

4.2.1 Testoperatingprocedures. All High Temperature Tests, the Cyclic Test. the Frost AccumulationTest, and the low Temperature test shall have the performance evaluated by the Air-Enthalpy Method on the indoor side. In 

### addition. the High Temperature Testand the Low Temperature Test shall have a simultaneous test method (as described in 4.1) 

### used as a check. The values calculated from the two methods must agree within 6 percentin order to constitute a valid test. Only the results from the Air-Enthalpy Method on the indoor side shall be used in the calulations in section 5.2.



### 4.2.1.1 Testprocedureforhigh temperature test. When the outdoor AirEnthalpy Method is used, the outdoor chamber must not interfere with the normal aircirculating pattern during the preliminary test. It 

### is necessary to determine and adjust for systemresistance when the outdoor air measuring apparatus is attached to the ou,tdoorportion ofthe unit. The test room apparatus and test units must be operated for at least one hour with at least Ih hour at equilibrium and at the specified test conditions prior to starting the test. The High Temperature Test shall then be conducted for
a minimum ofIh hour with intermittent data being recorded at lo-minute intervals. For all units. especially those having controls which periodically cause the unit to operate in defrost mode, attention should be given to prevent defrost during the HighTemperature Test. Units whichhave undergone a defrost should operate in the heating mode for at least lO-minutes afterdefrost termination prior to the start ofthe test. When the outdoorAir-Enthalpy Methodis used as a second test then a preliminary test must be conducted for a minimum of30 minutes with 4 ormore sets ofdata recorded at 10 minute intervals, all 

### remaining requirements of Section 3.6.1 

### in the ASHRAE Standard 37-78 

### shall then apply in conducting the " preliminary test for the outdoor air 

### enthalpy method. For some units, at the ambient condition ofthe test, frost may accumulate on the outdoorcoil. If

### the supply air temperature or the difference between the supply air temperature and the indoor air entering temperature has decreased by more than 1.50 

### F at the end ofthe test. the unit shall be defrosted and the test restarted. Only the results ofthis second HighTemperature Test shall be usedin the heating seasonal performance calculationin section 5.2. Prior to beginning the High 

### Temperature Test, a unit shall operate in the heating mode for at least 10 minutes 

### after defrosttermination to establish equilibri1.lm conditions for the unit and the room reconditioning apparatus. The High TemperatureTestmay onlybegin when the test unit androom conditions are within the test condition tolerances specified in Section 6.2.1 ofthis Appendix.



### 4.2.1.2 Testproceduresfor the cyclic test. The cyclic test shall follow the High Temperature-Test and by cycled "on" and "off' as specified in 3.2.1.2

### until steadily repeating anibient conditions are achieved forboth the indoor and outdoor test chambers, but for not less than 2 complete "off'/"on" cycles. Withouta breakin the cycling pattern. the unit shall be operated through an additional "off'/"on" cycle, during which the required test data shall be recorded. During the last cycle, whichis referred to as the test cycle. the indoor and outdoor test room ambient conditions shall remain within the tolerance specified in section 6.2.2. 

### ofthis Appendix. If, 

### prior to the High Temperature Test, the unit underwent a defrost cycle to rid the outdoor coil ofany accumulated frost. then prior to cyciing the unit "off' and "on" it should be made to undergo a defrost. After defrost is completed and before starting the cyclingprocess, the unit shall be operated continuously in the heating mode for a 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 and room 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 thefrost accumulation test. The defrost controls shall be set at the normal settings which most typify those encountered in Region IV as



### 11

### ARI STANDAR D 210-81

_

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 If2 hour prior 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 preliminal"J -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 one hour when the unit is operating at the required test conditions. the preliminary test period shall start at the termination ofa defrost cycle which automatically occurs and shaH end at the termination ofthe next automatically occurring defrost cycle. For units containing defrost controls which are likely to**cau~e** defrost at intervals exceeding one hour when operating at the required lest condition. the preliminary test period consi§ts of"healingonly" preliminary operation for at least one hour. after which a defrost may be manually

or automatically induced. The test period then begins at the termination ofthis defrost cycle and ends at the termination ofthe next automatically occurring defrost cycle. 

### Ifthe unit has not undergone a defrost after 12 hours. then the tests shall 

### be concluded and the results calculated for this 12-hourperiod. Forunits which 

### turn the indoorfan offduring dekost the indoor supply duct shall 

### be blocked during all defrost cycles to prevent natural orforced convection through the indoorunit During defrost. resistance heaters normally installed with the unit shall be preventedfrom operating.



### 4.2.1.4 Testproceduresforthe low temperature test. Where applicable. the High Temperature Testpreparation and performance requirements shall also be used in the Low Temperature Test. The test room reconditioning equipment shall first be operated in a steady-state mannerfor at least one-halfhour at equilibrium and at the specified test conditions. The unit shall then undergo a defrost. either automatic or manually induced. It is important that the unit 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 10minutes after defrost termination. the test shall start. Test duration is one-halfhour. For all units. defrost should be prevented during the one-halfhourtestperiod.



### 4.2.2 Testinstrumentation. 4.2.2.1 Testinstrumentationfor the high tempe!'Qture test. The indoor airflow rate shall be determined as described in Section 7.1 through 7.4 ofASHRAE Standard 37-78. This requires the construction ofan air receiving chamber and discharge chamber separated by partition in which one ormore nozzles are located. The receiving chamber is connected to the indoor air discharge side of the test specimen through a short plenum. The exhaust side ofthe air flow rate



### 12 measuring device contains an exhaust fan 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 oris ducted through a conditioning apparatus and then back to the test specimen inlet. The static pressure across the nozzles. the velocity pressure. and the static pressure measurements at the nozzle throat shall be measured with manometers which will result in errors which
are no greater than ±1.0percent ofindicated value and having minimum scale divisions not**exceedin~** :.0 percent ofthe reading. Static pressure and temperature measurements must be 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 errorno greater than ±0.2 percent in four places approximately 45 degrees apart around the nozzle in each oftwo places 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 ali other equipment components shall be measured with a watthour meter which is accurate to within ±0.5 percent ofthe quantity measured. Measurements ofthe air temperature**~ntering** and leaVing the indoor,coil or the difference between these two shall be made in accordance with the requirements of ASHRAE Standard41 part 1. These temperatures shall be continuously recorded with instrumentation having a total system accuracy within ±O.3° F ofindicated value and a response time of2.5 seconds orless. Temperature measurements are to 

### be made upstream ofthe static pressure tap on the inlet and downstream ofthe static pressure taps on the outlet. The indoor and outdoor dry-bulb temperatures shall 

### be continuously recorded with instrumentation which win result in an errorno greaterthan ±O.3° F of indicated value. The outdoorwet-bulb temperature shall be continuously recorded. Static pressure measurements in the ducts and across the unit shallbe made in accordance with Section 8 ofASHRAE Standard 37-78 using equipment which will result in an errorno greater than ±0.01 inch ofwater. Static pressure measurements shall 

### be made and recorded at S minute intervals. All other data not continuously recorded shallbe recorded at 10minute intervals.



### 4.2.2.2 Testinstrumentationfor the cycling test. The airflow rate during the onperiod ofthe Cyclic Test shall be the same agreed within ±1. percent as the airflow rate measured during the previously conducted High Temperature Test. All other instrumentation requirements are identical to 4.2.2.1 ofthis Appendix.



### 4.2.2.3 Test instrumentationfor thefrost accumulation test. The airflow rate for the FrostAccumulation Test shall be the same as described in 4.2.2.1. The indoor-side dry-bulb temperature and outdoor-side dry-bulb temperature shall be continuously recorded with instrumentation having a total system accuracy within ±0.3° F ofindicated value. The outdoor dew point temperature shall be determined with an errorno greater than ±O.SO F ofindicated value using continuously recording instrumentation. All other data shall be 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 dermed as the actuation (either automatically ormanually) ofthe controls normally installed with the unit which cause it to alter its normal heating operation in order to eliminate possible accumulations of frost 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 in capable ofrecording the cooling done during defrost as well as the total electrical energy usage during defrosl. These data and the continuously recorded data need be the only data obtained during defrost.



### 4.2.2.4 Test instrumentationfor the low temperature test. Instrumentation for the Lew 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 tbe high temDerature test. All tests shall be conducted within the tolerances specified in Section 6.2.1. Variation greater than those given shaH invalidate the test. The heating capacity results by the indoorAir Enthalpy Method shall agree within 6percent ofthe 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 tolerances 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 tesL 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 unitis 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 Sminutes 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 shall be 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 tesL 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 Testingproceduresforairsource units whichprovide bothheatingandcooling.

### _________________________ARI STAN DAR 

### 0 210-81

The testing procedures for units which provide both heating andcooling shall be the
same as those specified in Sections 4.1 and 4.2 ofthis Appendix. Also during the offperiod ofthe dry-coil cooling test (test D). the switch-overvalve shall remainin 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 at47° F. the switch-overvalve shall remain in the heating mode. unless the controls normally suppliedwith the unit are designed to reverse it. 

### in which case the controls shall operate the valve.



### 4.4 Testingproceduresfor watersource units whichprovide bothheatingandcooling. (Reserved)



### 5.0 Calculationsforperformancefactors. 5.1 Calculations of seasonalenergy efficiency ratios (SEER) in air-source units.

The testing data and results required to calculate the seasonal energy efficiency ratio (SEER) in Btu's per watt-hour shall include the following:

(i) Cooling capacities (Btu/hr) 

### from tests A and B and. ifapplicable. the cooling capacity (Btu/hr) from test C and the total cooling done from test D (Btu·s). 

### Q

..k 

### (95F] 

# Ouk (82F) 

## Q

.., dry Qeye. 

### dry (ii) 

### Electrical powerinput to all components and controls (watts) from tests A. B. and 

### ifapplicable the electrical power

, input to all components and controls '(watts)

from test C and the electrical usage (watthour) from testD. 

# E."k (95F] 

## E..k (82F) 

# E..k
• 

### dry 

### Ec.c. dry

(iii) 

### Indoorair flow rate (SCFM) and external resistance to indoorair flow (inches ofwater).

(iv) Air 

### temperature (" F] Outdoor dry bulb Outdoorwet bulb Indoordry bulb Indoorwet bulb

Where thepooling capacities 

### Quk 

### (In!F). from test A. 

### Quk (82). from test B. and 

### Qu, dry. from test C. are calculated using the equations specified in section 3.7 

### ofASHRAE Standard 37-78. 

### The total cooling done. 

### Q""

.. dry 

### from testD. is calculated using equation (1) below.

Units which do not have indoor air circulating fans furnished as part ofthe model shall have theirmeasured total cooling capacities adjusted by subtracting 1250 Btul 

### hrper 1.000 CFM ofmeasured indoor air flow and adding to the total steady-state electrical powerinput 365 watts per 1.000 

### eFM of measured indoor airflow. Energy efficiencyratios from tests A. B. and C. EERA•

### EERa. EER

... dry respectively,
are each calculated as the ratio ofthe total cooling capacityin Btu/hrto the total electrical powerinput 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 equipmentpower shall be 1250 Btu/hr

### per 1.000CFM ofcirculating indoor air. The energy usage required in one complete cycle requiredfor indoor air circulation is the product ofthe circulating indoor air equipmentpower and'the duration oftime in one cycle that the circulating indoor air equipment is on. The total cooling done shall then be the measured cooling in
one complete cycle minus the energy usage required for indoor air circulation in one complete cycle. The total electrical energy usage shall be the sum ofthe energy usage required for indooraircirculation in one complete cycle and the energy used by the**r~maining** 

### .equipment components (compressor{s). outdoorfan. crankcase heater. transformer{s). etc.) 

### in one complete test cycle.

Energy efficiency ratio from tests D. EER""c 

### dry is calculated as the ratio d 

### ihe total cooling done in Btu's to the total electrical energy usage in watt-hours.



### 13

### AR I STAN DA R 0 

### 210-8.

_

PLF(0.5)

## = 1-0.5X CD Q:.-2(Ti)

- BL(Ti) (f..-'( Ti) -Q:.-'( Ti) (1) where

The value of the degradation coefficient. Cl',-' for low compressor speed cycling and 

## ct-· for high speed on/off compressor cYlJling 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= 1) for which the steady-state cooling capacity, 

### Q':.-' (T i), is great€r than or equal to the building cooling load, BL (T i), evaluate the following equations:
Xi-l BL(T;) (f..-I( Ti)

(1) Xl-t-Load factor

. B L(Ti)=Bullditlgcoolingload (Btu/hr) attempera- ture (Ti) from section5.1.3. Q

..l-J(Ti)=Steady-state cooling capacity (BtU/hr) at temperatures (Ti) from section 5.1.3.

(2) Xk-'=l-Xk-l
(3) Q<ffi) =[Xk-1X<l..-I(Ti)

+Xk-·X

### Q~;'(**Ti)]X~** (4)

### E<;i)=[Xi-1XE~._1(Ti) +Xk-·X

### E~.~'(**Ti)]X~** PLFk-l= 1-Cl',-'(l- Xk-l).
Where CD the degradation coefficient as described in section 2.1.3 or as calculated above in equation (1). 5.1.3.2 When a unit must alternate between high (k=2) and low (k= 1) compres- sor speeds to satisfy the building cooling load at a temperature 

### Ti, evaluate the following equations: where

E(Tj)

. . 

### -N

# = ratIOofEnergyusage{watt-hr.) III temperature binj to the number oftemperaturebinhours. (3) (2) Q<ffi)=Xk-1XQ:;'(T;)XN

where

Q7;i)

### = ratio of total cooling (Btu) in temperature binj to the number oftemperaturebinhours.

"'j is the fractional number of bours in temperature N binj from 6.1.2.

5.1.3.3 When a unit must cycle on and off at high compressor speed (k=2) in order to satisfy the lmilding cooling load at a temperature 

### T;, evaluate the equations provided in sect.ion 5.1.3.1 replacing (k=l) data with the (k=2) data. 5.1.3.4 When a unit operates continuously at high compressor speed (k= 2) at an outdoor temperature 

### Ti evaluate the following equations:
(1) Q<;i)

### = (f..-2( T;) X

# lJ

E(Ti )

_ El-'( T.) X

N

- u 2 N (2) energy efficiency ratio (SEER) for units employing single-speed compressors and multi-speed condenser fans shall be based
on the energy efficiency ratio obtained for test B and the method outlined in 2.1.2 of this Appendix 

### to account for the perform-
ance under cyclic conditions. The energy efficiency ratio for test B is obtained with the unit operating with the condenser fan speed which normally occurs at test B ambient conditions.

The seasonal energy efficiency ratio in Btu's/watt-hour shall be determined by the equation: SEER=PLF(0.5) X EERB

where

Q

..l(ll5 F)=Bteady-state capacity measured from test A as outlined in 2.1.3. /;/u'(82 F)=Btelldy-state capacity measured from test B as outlined in 2.1.3.

wben where

CD=Tbe dClll'lldation coefficient described in 2.1.2 or as calcUlated in equation (4) above. 5.1.3 Method for calculating a SEER for units with two speed compressors or two compressors, or cylinder unloading. The calculation procedure described in this section shall be based on the performance of test A and B at each of the compressor speeds for two-speed compressor units, subject to the conditions on condenser fan speed 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 = 1 (and the term "low-speed") designates the com- pressor that normally operates at an outdoor dry-bulb temperature of 82° F and 1=2 (and the term "high speed") denotcs operation with both compressors.

In order to evaluate the steady-state capacity Qui ( 

### Ti), and power input, Eui(T i), at temperature T i for each compressor speed, k=l, k=2, the results of tests A and B from 5.1 shall be used in the following equation: 

### Q

• ."(Ti)=Q•."(95 F) 

## +Qui (82

### ~~=~:/ (95 F) [33-(5Xj)]

where

Q,.·

..(llIl F)=Bteady-state capacity measured from test A in 2.9 at the high compressor speed. PLF(O.5)

## = 1-0.5X CD where EERB=energy efficiency ratio determined from test B In 2.8 PLF(O.f» = Part-load performance factor as determined from the equation:

Eu l(llIl F)= Electrical power Input measured using test A as outlined in 2.1.3.
E u l(82 F) = Electrical power input measured from using test A as outlined in 2.1.3. The building cooling load BL (T i) for the four cases described in section 5.1.3.1 through 5.1.3.4 shall be obtained from the following equation: BL(T)=**(5Xj)-3XQ:·~'** (95 

### F) '95-65 

### 1.1 EER,yc.d,y EER

... d,y l-CLF 1 C

D

## = (4) (1)

(3)

where CLF=coolingload factor. Q

.. '" =Total steady-state coolingcapacityfromtestC (Btu/hr). T=Duration of time (hours) for one complete

cycle consisting o( one compressor H on" time and one COID.pressor Hoff" time. The results of the cyclic and steadystate dry-coil performance tests shall be used in the following (4) equations:


### 60X'VXC""xr QCYC.d

....

### =[V,,'X(l+ W,,)]

where

CD=Isthe degradation coefficient described in 2.1.1 or as calculated in equation (4) above.
5.1.2 Method for calculating a SEER for units with single-speed compressors and multi-speed condenser fans. The seasonal where

Q

.... d,,=Total cooling over a.cycle comisting ofone compressor "off"**~nod** and one compressor

. "on" period (Btu s). V=Indoor air flow rate (cfm) at the dry-bulb temperature, humidity ratio, and pressure existing in the region ofmpssttrement. C••=Specific heat at constant pressure of air- water mixture per pound of dry air, (Btu/lb-°F). V.'=Specific volmne of air-water mixtttre at the

. same dry-bulb temperature, humidity ratio,

and pressure used in the determination of the indoor sir flow rate (ft'/lb). W.=Humidity ratio (lb/lb). and 

### r (hr.-OF), which is described by the equation: (2)



### r 

## = f(tlme Indoorfan off) [Ta1(t)

- Ta2(t)]dt 

## J (time Indoor fan on) where

T.I(t)=Dry bulb temperature of air entering the indoor coil (OF) at time (I). T.2(t) =Dry-bulb temperature ofairleaving theindoor coil ("F) at time (t).

where EERs=Energy efficiency ratio determined from test B as outlined in 2.1.1. P LF(O.5)= Part-load performance factor when cooling load factor=O.5 as determined from the equation: The preceding equations are then used in the following equation to calculate a degradation coefficient CD rounded to the nearest .01.

where

EER.•. d••= Energy efficiency ratio from test C. (Btu! watt-hr). 5.1.1 Method for calculating a SEER for units with single-speed compressor and single-speed condenser fans. The seasonal energy efficiency ratio for units employing single-speed compressors and single-speed condenser fans shall be based on the performance of test B and a method outlined in 2.1.1 and 3.1.1 of this Appendix to account for the cyclic performance.

The seasonal energy efficiency ratio in Btu's/watt-hour shall be determined by the equation: SEER=PLF(0.5) XEERB



### 14

## _________________________ARI STAN DARD 210-81

where



### X [T a2(t)

- T.I(t)!dt lating, and the average flow rate of indoor air circulated in units of 1000 SCFM.



### 15 COP. y .(47) COP••(47) I-HLF

Q.y.(47) 

## Q

••(47)XT 1

HLF 

### CD (1)

The actual heating done during the Cyclic Test, 

### Q.,.•( 47), shall be determined using the following equation:
60XVXC""xr 

### lV"IX(l+W,,)]

V=the flow rate during the on-period calculated in accordance with section 7.4 ofASURAE Slaud· ard 37-78in CFM. Cpo=Specific heat at constant pressure of air-waler mixture perpound ofdry air, (Btu/lb-°F). V

o'=Specific volume ofair-water mixture at the same dry-bulb temperature. humidity ratio. aud pressure used in the detennination ofthe indoor air flow rate (ft'/Ib). W.=Humidity ratio (lb/lb). and 

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

# f (time indoorfan off) 

### r = . . [T. 2(t)

- T.I(t)]dt (time mdoorfan on) where

Tol(t)=Dry-bttlb temperature ofair entering the indoor coil (OF) at time (I). To,(t)=Dry-bulb temperature of alr leaving the indoor coil (OF) at time (I). The net heating, QDEF {35) in Btu's done dming the test period shall be determined using the following equation:

CD=thecyclicdegradationcoefficientroundcd to the nearest .01 COP cy.(47) as defined above COP

..(47) as defined above HLF is the heating load factor calculated as follows: where 

# v=the average ofthe alr flow rate calculatedat four or more time intervals throughout the healing phase ofthe test usiug the equation iu section U ofASHRAE Siandard 37-i8. Cpo=Specific heat at constant pressure of air-water mixture per pound ofdry air, (Btu/lb-OF). Vn'=Specific voltune ofair-water mhture at the same dry-bttlb temperature, humidity ratio, and pres- sure used in the determination oflite indoor air now rate (ft,!lb). Wn=Utunidity ratio (lb{lb). and 

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

# f

<time ofnext defrost termination) 

## r= (time ofdefrost termination

(3) where

To'(I)=Dry-bulb temperature of air entering the indoor coil 

### <0F) at time (I). To'(I) =Dry-bulb temperature ofairieaving theindoor coil eF) at time (I). The cyclic degradation coefficient shall be calculated as follows:

where 

### (2) Units not having an indoor fan as part of the model tested shall add 1250 Btu/hI' per 1,000 SCFM of indoor ail' handled to the measured capacity to obtain the total heating capacity, 

## Q

..(17), 

## Q

..(47) or 

## Q

..(62), and add 365 watts per 1,000SCFM of indoor air handled to the measured power to obtain the total power input, 

## B

.. (17), 

## E

..(47)
, or 

## B

.. (62), to the unit.

The coefficients of performance (COP) for the High Temperature Tests COP••(62) or COP

..(47), and Low TemperatUl'e Test, COP

..(l7), are calculated as the ratio of the heating capacity in Btu/hI' to the product of 3.413 and the power inputs to the indoor fan in watts and the power inputs to the remaining equipment com- ponents (including all controls) in watts.

Units which do not have indoor air circulating fans furnished as part of the model shall have their total heating done (Q.y.(47» and energy used 

### E.y.(47) in one complete cycle adjusted for the effert of circulating indoor air equipment power. For units tested without an indoor fan as part of the model, Q.y.(47) shall he increased by a quantity of heat equal to the product of 1250 Btu/hr per 1,000 SCF:YI, the length ofthe on-period ofthe test cycle in hours, and the flow rate of indoor air circulated in units of 1,000 SCFl\1. The total energy usage, 

### E.y.(47), shall be the sum of the energy usage required for air circulation during the test cycle and the energy used hy the remaining equipment components (including all controls) during the test cycle. Units not having 

### an indoor fan as part ofthe model tested, shall set the energy required for indoor ail' circulation equal to the quantity given by the product of 365 watts per 1000 SCFM, the length of the on-period ofthe test cycle in hours, and the rate of indoor air circulated in units of 1000 SCFM.

The cyclic coefficient of performance, COP.y.(47) is calculated as the ratio of the total heating done (Q.y.(47» in Btu's to the product of 3.413 Btu/watt-hour and the total energy usage (E oyo(47» in watt hours. The net heating· capacity, QDEF(35) (Btufhr), is the total net heating done over the test period (including any credit for the indoor fan heat) divided hy the total length of the test period, in hours. For units with "demand defrost control system", the net heating capacity, QDEF(3.'i), shall be multiplied hy an enhancement factor of 1.07 to compensate for improved performance not measured in the Frost Accumulation Test. For units tested without indoor fans, the value determined for (jDEP(35) below shall he increased by a quantity of heat equal to the product of 1250 Btu/hI' per 1000 SCFM, the length of time in hours during the Frost Accumulation Test that there was indoor ail' cil'- culating, and the average flow rate of indoor air circulated in units of 1000 SCFM.

The total energy usage, EDEF(35) shall he the sum of the energy usage required for indoor-air circulation oming the test period and the energy useo hy the remaining equipment components during the test period. Units not having an indool' fan as part of the model tested, shall set the energy required for indoor ail' circulation equal to the quantity given hy the product of 365 watts per 1000 SCFM, the length of time in hours during the Frost Accumulation Test that there was indoor air circllas determined at each temperature bin according to the applicable conditions described in sections 5.1.3.1 through 5.1.3.4 as folloVl'S: 5.1.3.5 Calculate the SEER in Btu's/ watt-hr. using the values for the terms Q(T;) 

# z;r

5.2 Calculation of Heating Seasonal Performance Factors (HSPF) for AirSource Units. The testing data and results required to calculate the heating seasonal performance factor (HSPF), in Btu's per watt-hI', shall include the following: (i) Heating capacities (Btu/hI') from the indoor air enthalpy method fOl the High Temperature Tests, and the total heating done (Btu's) for the cyclic and frost accumulation tests. 

## Q

..(47) or 

### Q •• (62). 

## Q

.. (17). Q.y.(47). QDEF(35). (ii) Electrical powel' input to all com- ponents (watts) for the steady state tests, and the electrical usage (watt-hours) for the cyclic and frost accumulation tests



### k

.. (47) or 

### E

.. (62). 

### k••(17). 

### E.y.(47). 

### EDEP(35). (iii) Indoor air flow rate (SCFM) and external resistance to indoor air flow (inches of water). (iv) 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 37-78. Where the heating capacities 

## Q ••(47), 

### Q

•• (62) and 

### Q

.. (I7) and the indoor air flow rate are calculated using the equations specified in section 3.8.1 and 7.4 of ASHRAE standard 37-78. The total heating done, Q.y.(47) and Q(DEP35) are calculated using the equations below. 

# ± Q(T;)
. 1 

### N SEER-,,-:J=,.:c---



# -± E(T;)

j=l 

### N
5.1.4 Method for calculating a SEER for units with two speed compressor, two com- pressor or cylinder unloading capable of varying the sensible to total capacity (S/T) ratio. Multi-speed compressor and twospeed compressor units capahle of varying the sensihle to total capacity ratio (SIT) shall have the seasonal energy efficiency ratio determined as described in section 5.1.3. For such units, the mode of operation selected to c1etel'mine the steady-state capacities 

### Q

..k(95), 

### Q

..k(82), E••k(95), E

..k(82), and power inputs at each com- pressor speed k= 1, k=2, for tests A and B is outlined in section 2.10. 

### E(T;) 

## ""f./ and

### r



### ARI STANDAR D 210-81,

_

where 

# lJ BL(T;) J HSPF

:z: as defined in 5.2.1 j 71; N as defined in 5.2.1 Tj as defined in 5.2.1 where

{ . (65-T oD) Ql;g2)(47) 60 ,for regions I,



## = II, III, IV, and 

### VI**Q;~-2)(** 47), for region V 

### wtlcr

.. 

### Q

..(47) and 

### 1t'•• (47) and QDE,.,(35) Ilnd 

### £

..(47) and 

### Q

..(17) and 

### 1t'

..(17) are the capacities (in Btu/hr) and**pow~rs** (in watts), meallured during the High Temperature Tellt, the Frost Accumulation test, and tht Low Temperature Test, respectively.

'For each of lhe six regions specified in sec- tion 6.2.5, calculate the heating seasonal performance factors and seasonal operating costs corresponding to the standardized maximum and minimum design heating requirements and for all other standardized design heating re- quirements (see section 6.2.6) belween the maximum and the minimum. 5.2.2 Calculation of the heating seasonal performance factor (HSPF) 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:

and BL(T;) is thp huilding load at temperature 

### T;, in Btu/hI', calculated by:

BL( Tj )

## =(6~5~**:£~)** X(C)

## X(DHR)

where (C}=O.ii is a correction fact.or which tends to improve the sgre.ement between calculated and measured building loads (DHR}=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 DHRin section 6.2.Vin Btu's per bour where (minimum design heating requirement)

and (maximum design heating requirement) 

# {2ilk-2(47) {65- TaD) f . I

"".. 60' or regIOns ,



## = II, III, IV and VI

. 2.2Q:-.-2(47) for region V
where

<2

.. U-7) (4i) is the heat pump capacity measured during the high temperature perlormance test at 4;oF, with the unit operatine at the high compressor speed or with both compressors in operation, in Btn/hr Too is the outdoor design temperature gi"en in section 6.2.4 in degrees OF. and

17°F<T;<45°F



### (E

..( 47) 

### -E

..(l7» 

## E

..(l7) 

## +**3~(T;-17),** T;'?,45°F or T;S;17°F 

### (EDEF(35)

- 

## E ••(l7)) 

## E**·(1~)+** X(T;-17)

IS , 18'
17°F<T j<45°F (QDEF(35) 

## -Q

..(7» Q . (17) 

# + X(T j-17)

'" 18' (Q,,(47) 

### -Q

..(7»

. Q,,(7)+

### 3~(T;-17), T;'?,45°F or T;S;17°F

### Q(T~) >1 (3.413)(E( T;»

- 

# j BL(T;)

. X(T;)= Q(.T;) iQ{T;)'?,BL(T;)
1; Q(T;)S;BL(T j ) Q(T;) 1

or (3,413)(E( T;» <

TOFF=the outdoor temperature that the compressor is automatically shut off at (If no such tempera- ture exists, Tj is always greater than Ton and To,;.) TOI<=the outdoor tempemlllre that the compressor is automatically turned on (if applicable) if designed for low temperatnre automatic shutoff. Co=degradation factor determined described in section 5.2 and 2.2.1. 0; 

### T; S; 

### TOFF

PLF(X)=l-C D(l-X( Tj»



### . n· [BL(T;)-Q(T;)X(T;)6(T;»)-N' RH(T j ) N 3,413 where



### <I" (4i) is the heat pump capacity measured during the High Temperature Test @ 4;0 F TOD is the outdoor design temperature given in section 0.2.4

and

## Q(T~) >1 (3,413)(E( T;»

- and maximum design heating requirement

{ . (65- TaD)

.

2Q

..(47) 60 ' for regIOns I,



## = II, III, 

### IV, and VI 

# 2.2Q

..(47), for region V

E(T;)= Q(T;)=

In using the above equation to calculate HSPF, the heat pump capacity in Btu/hI', 

### Q, and the power in watls, 

## E, shall be obtained as follows:**~n;** X(T,)

.

### ~N PLF(X) 6(T;)E(T;)

### +~ RH(T;)] i 

### N where

Q",(47} as defined above

Q

..(4i} as defined above

T=Dwation of time (hour.<) for one complete

cycleconsisting ofone compressor "on" time 8ud one compressor "oft" time.

BL(T;) J

where (minimum design heating requirement)

{ . (65-TaD) _ Q

..(47) 60 ,for regions I,

- II, III, IV, and VI 

### Q

..(47), for region V i=l,2,3, ..• , n corresponds to theit. tempera-

ture bin. n=total number of non-zero temperature bins

in the climatic rcgion. Tj=(fii-5j) is the representative temperature of theit. bin, (oF). :&=indicated the Quanlit.y following the symbol j is to be summed overall temperature bins. RH(Tj} =supplementary resistance heat term at

N temperature Tj required in thosecases where the he.at pump automatically turns off (Tj<T.,,) or when it is needed to meet the balanceoftbebuilding beating**requir~ments.** n' (watts).**~=iS** tbe numberofhours in thej'. temperature

• bip. divided by N=:& OJ and is referred to l>S 

### , the "fractional hoursinjt. temperaturebin". 30413=is a conversion factor whicb converts watt hours to Btu. BLCTj}=building load at temperature Tjn (Btu/hr).

6(Tj}=heat pump low temperature cut-out factor. X(Tj}=heat pump heating load factor. PLF(X}=heat pump part load factor.

The Quantities BLCT j)
, 6(T;), X(T;), PLF'(X)"and where

RH(T;) N

are defined by the following equations:
BUT;)

## =(6~5~**:£~)(C)** (DHR)

where (C}=O.77 is a correction factor which tcnds to improve the agreement between calcnlated and measured building loads (DlTR}=the minimum and maximum design heating requirement which the heat pump is likel)' to enconnte.r when installed in a resid2f'.t"e" rounded offto the neareststandardized D H R in section U.2G in Btu/lIr 5.2.1 Calculation of the heating seasonal performance factor (HSPF) for air-
source heat pumps with single speed compressors. For each climatic region listed in section 6.2.4, and for design heating requi!'ements equal to both the sl.andardized minimum lind maximum design heating requirements de1iDed below, calculate the HSPF defined
as: 'HSPF

'These items have been corrected in accordance with a letter from the Department ofEnergy, dated December 7, 1980.


### 16

## _________________________ARI STAN DARD 210-81

NOTE: The sup€rscript'(A:=I)and (1:=2) refer to the heat pump opera.ting at low speed or single compressor operation and high speed or two -compressor operation respectively.
E(N

T1) is theheat pwnpelectricalenergyusageinthe jtb temperature bin divided by the total nwnber o(bin hollrS and is evalnatedaccording to the (onr possible case!l o( heat pwnp operation denoted below in _tts. RHN'(T;) as defined In 5.2.1 and is evaluated according to the Cour possible o(heat pwnp operation denoted below (in watts). 

### ClUe I.-Units operating at low compressor speed or with a single compressor, i.e., k= 1, for which the building heating load, BL(

### T;) is less than or equal to the heating capacity, 

### ¢-t-l(Tj ). BL(Tj ) Qk-l(T;) E(T j ) Ek-I(T j)Xk-l(T j)8'(T j) nj 

# -r= PLFk-l 

## N Case III.-Units cycling on and off at high compressor speed or cycling both com- pressors on and off together (k=2) in order to satisfy the building heating load at temperature 

### Ti• Qk-t( Tj)<BL(T,)<Qk-2(Tj )

Ek-2(

### Tj )Xk-2(Ti)

### 0" ( Ti)

# lJ

PLFk-2

### ~B L(Tj )[l- &" (Tj »)

3.413 . (1..-1 (47) (Q:.-1{62)-ll..-1{47» X (Tj -47).**+-----;1;-;5i-'-'--'--~**,**~.-1(l7) (Qbi:~(35)**  -**~.-1(17»)** 

### X (T·-17) 

## + 18';
170**F~Tj<40o** 

### F 

## tl.- 1 (17)**(~;l** (47)

- tl.,-I( 17» X(T·-17) 

# + 30 ' ; Tj <17° F

RH(T;) 

# lJ BL(T j)[l-&'(T;») N 3.413 Xk-l(T;) BL(T;) 

### ¢-t-I( T;) PLFk-I=1-G,-1(1-X7- 1)

{ O;**Tj~** TOFF

## &'(T;)=~;**TOFF<T;~ToN**

1; 

### T1>ToN


### Case II.-Units alternating betweenhigh speed or two compressor operation (k=2) and low speed or single compressor operation (k= 1) to satisfy the building heating load at temperature 

### Tj • cjk-I( T;)

# < BL( T;)

# <(j<-2( T;) E<J;) = [Ek-l( T;)Xk-l(

### Tj ) 

# +Ek-2( Tj)Xk-2(

### Tj »)&'( T/ )

RH(T;) 

# !jJ BL(Tj)[l-&'(T i)] N 3.413 Qk-2( T;)

- BL(

### Tj ) Xk-l(

### Tj ) Qk-2(Tj)_Qk-l( Tj) Xk-2( Ti)= I-Xpl( T;)



### {O;**Ti~** 

### Ton

## 6'(Tj)~; TOFF<Ti5:.ToM



### 1; T;>ToN { O;**Tj~ToFF** a"(T;)=

## ~;**TOFF<T;~ToN** 1; Tj>ToN 

### Case IV.-Units operating continuously at high compressor speed or with both com- pressors in continuous operation (k=2) in order to satisfy the building heating load at temperature Tj • BL(T;) ';?Qk-2(T j)

E<:i) =Ek-2(Tj)Xk-2( Tj)o"(Tj ) 

# lJ

RH(T;) N [BL(Tj) - Qk-2(Tj)Xk-2(Tj)&"(Tj»)

# lJ

3.413 Xk-2(

### Tj ) = 

### 1.0 0;**T;~** TOFF

or Qk-2(T / ) <1 (3.413) (Ek-2(Tj 

## »

## ~; Ton' Tj

### 5:. TON &"(T,')

## = Q' (T) d 

## '-2 j 

### > 1
an (3.413)(Ek-2(T i)
1; Tj';? TON d Qk-2(T;) >1

an (3.413)(Ek-2(T j

# »)

Where in each of the above cases X(T;)=heat pnmp heating load (actor. PI,F=heat pnmp part load (actor (not reqnired [or cases 11 and IV.) 6"(T;)=heat pmnp low tempcratnre cnt-ont (actor. To" as defined in 5.2.1. Too as defined in 5.2.1. Cvl -1=th. part load degradation [actor described in section 2.2.1 and 5.2 [or the nnit cyding at high eompressor speed or with both com- pressors simnltaneonsly cycling (if applicable). Cv (l-I) = the part load degradation [actor described in seclion 2.2.1 and 5.2 for the nnit cycling at low compressorspeed orWilh the singlecom·**~r** that nonnally operates atlow heating**Q~-'(17) (~.-'**  (47)

-**Q~.-'(** 17) X (T·-17) 

# + 30';

Qk-2 (Tj ) 

## = Q':.-'(17)
(€loEH35)

- 

## il..-'(17) X(T;-I7). 

# + 18 '
17° F<T j<45° 

### F


### E;;'(47)**(E~;l (62)-~-1(47)** 



# +**~X.:...:('-T-'-;--47---:.)** . 15 ' Tj ';?400 

### F**E~;'(17)** (EbEH35)**-E~;'(17»)** 

# +**--.-;~X.:...:('-T..:..j--17---:.)** . 18 '



### (E:;'(47)

-**E~-'(** 17» 

# +**--:-:~X.:...:('-T..:..;-_17-'-)** . 30 ' T j<17° 

### F**E~;-2(17) (E~-2(**  (7)

- E';.-·(17») 

# +**~X...:....:...(**T-!-;-_1_7-,-). 30 ' Tj ';?45° F or Tj5:.lio F**E~.-·(17)** (Ett-}(35)

-**E~,-'(17»** 

# +**~-::X-,--,-,(**T::...<;_-_l___:.7)

. 18 ' 17° F< T;<45° F 

### 17

### AR I STAN DA R 0 210-81

_

For each of the six regions specified in section 6.2.5, calculate the heating sl'asonal performance factors anel seasonal operating costs corresponeling to the stanelarclized maximum and minimum elesign heating requirement!! and for all othl'r standardized design heating requirements (see section 6.2.6) between the maximum and the minimum. 

## s.a CalculatiOlll1 of the Actual Repr6llentatitle Region41 Annual Perfonnance Factorll for Air Source Central Air Conditione", (Heal PumplI) Which Prol'ide Both Healing and Cooli1Jg. 5.3.1 Calculation of actllal regional annual performance factors (APFA) for a particular location and for each standarelizeel (Iesign henting requirement. (CLH A ) (Q.l(95F» (APF )=**~(HLH.'>(DHR)(C)** .• (CLH A)(Q.!(95F» (SEER) 

# +(HLH

.. ) (DHR) (C) (HSPF)

where (eLHA) Is**th~** ll<'lnal coolinI': load honrs {or the p8rtirn)ar Ioration, determinE<! {rom the

• map in 8I'<'lion 1;.1.3. (Q..'(95F» is defined in 5.1. (DHR) is defined In 5.2.2. (e) is defined in 5.2.2. (HLHA) Is the actnal htoeUnf( load bonrs {or the**parti~ular** Ioration**d~lermined** from Ibe map in _lion 6.2.5. (SEER) is the eeasonal**en~rgy ~mci~nry**  rallo detennined in _lion 5.1. (1fSPF) is the htoetinf(_nal**~rtormanl'f'** (aetors as detennhlt'd in _tion 5.2 lor_·h sland· ardized design htoeling**reqnirem~nt** within the**parti~lllar** Iorallon's region or for the ll<'tnal design heating reqniremrnt if known. where the particular location'll region is determined from the map in section 6.2.,') and, the standardized design hf'ating re- quirements within the rl'gion are (Ietermined in sections 5.2 and 6.2.6. 5.3.2 Calculation of rcprcscntativt' re- gional :lOnllal pelformance factors (APFR) fOI' f"al'h rE-gion and for each standardized design heating re- quirement. (CLH R) 

### (Q••t(95F» 

## +(HLHR)(DHR)(C) (CLHR )(Q.!(95F» SEER 

# +(HLH R ) (DHR)(C) HSPF (Q.-'(llIjF» Is dellned In 6.L (DHR) is dellned in 502.2. (e) II dellnedin 5.2.2.



### 18 where (eLHa) III tbe represenlatln cooUng load bours for eaeh healing load houn region, as deter· mined in _lion 6.3- (HLHa) is the representative heating load hours (or each region as determined in &ecUon 6.2.5. (SEER) is the seasonal energy elDcieney ratio as determined in aeolian 5.1. (HSPF) Is the healing seasonal performance laelor as determined in seelion 5.2 for eaeh region and for each standardized design healing re- quirement within each region. where the regions are listed in section 6.2.5 and, the standardized design heating re- quirements within the regions are fletermined in sections 5.2 and 6.2.6. a.4 Calculations of Seasonal Energy Efficiency Ratio lor Water Souree UniUi Which Provide Both Heating and Cooling. (Reserved) 

## a

..') Calculation of Heating Seasonal Performance Factor for Water Source UniUi Which Pro/'ide Both Heatil/g and Cooling. (Reserved) ,').6 Calculatioll of Annual Performance Factor For Water SOllree UniUi Which Provide Both Healing and Cooling. (Reserved)

BlWHG COIlE 1450-0,

....

# -

6.0 Reference Material

6.1 Coolinq reference material 6.1. 2 

### -Distribution of fractional hours in temperature bins to be**use~** 

### for calculation

of the SEER for 2-speed compressor and 2- compressor units

-Test operating and test condition tolerance for cyclic dry-coil tests

Test operating tolerance (total observed

range) 1 ••... 65 to 69 .•. 67 .214 2 ••••• 

### 70 to 74 ••• 72 

### .231 3 ••••. 

### 75 to 79 .•• 77 

### .216 4 .•••. 80 to 84 ••• 82 .161 5 .••.. a5 to 89

... 87 .104 6 .•••• 90 to 94 •.• 92 .052 7 .•.• , 95 to 99 .•• 97 ;018 8 ••••• 

### 100 to 104. 102 .004 6.1.1**Rea~ings,** 

### remarks

Outdoor dry-bulb air temperature, Fahrenheit: Entering ••••••••••••••••••••• Indoor dry-bulb air temoerature, Fahrenheit: Entering ••.••••.••.•..••. '"

. Indoor wet-bulb air temperature, Fahrenheit: Bnterilig •••••••..•••...••.••. After the 1st 30 Sec after
comnressor startup. External resistance to airflow, inches water••.. Nozzle pressure drops, percent of reading ..••..•. Electrical voltage inputs to the test unit, percent. 2.0

2.0

(* )



### 0.05

2.0

2.0 Test condition tolerance (variation of average from specified test condition)

0.5

0.5

(* )



### 0.02 Bin temperature range (degrees Fahrenheit)

Bin No., j: 

### Representative temperature

bin fol' (degrees Fahrenheit) Fraction of 

### total temDeratur.e bin hours**n.i/~!**



## ..... \0 

### * Shall at no time exceed that value of the wet-bulb ternoerature which results in the oroduction of condensate by the indoor coil at the dry-bulb temperatura existing for the air enterina the indoor portion OF 

### the unit. 

# :a- :2J



# en -t

# :aZ C 

# :a- :2J C
I\)
«:) I C»

### A'.skl 

### - 0 Cooling Load Hours Cana' Zone

- 6.000 

# .. .. 

# .. Guam

- 6.600 

### Hawaii



# - 2.300 

# .. 

# .. Puerto Rico

- 6.000 SI"'OO



### - 6.600 

# .. 

# .. 

# .. Virgin 'sland

- 6.000 

# .. 

# .. 

# .. N 

### o 

# 88 0 "'- " 0 

# " 6.1. 3 

## Distribution of Actual**Cooli~g** 

## Load Hours (CLH

# n) Throughout the**U~ilcd** 

## States



# - • ::D



# - C/) -4 

# • Z C 

# • ::D 

### C
I\,)



# .... o I 

## co



# ....Beatiog**Refe~eoce** Material 6.2
6.2.1 Test op.rating aDd t.st coadit1on tol.ranca for 6.2.2 Tast. oneratUS-**and-t..eat_J::o~** t0111"nc

..**~r** the-

..n-period portion of. e)lclie ,ollrfocnanca,

_ _ ._.

Staadr-Suu**Il~h T~at1tte**  Tes: lu 47·' (8.3·C) or 62·F (16. 7·C») .N L....,., T""'i"'rllt'=e Tut !n 17·F (-S.3·C») Te.t Op.rating Tol.ranc••

- (Appllas alt.r th. lat 

### 36

••c. aft.r compr•••

# or atart-up) Tut Condition T"lerance w",-



### ** T ••t Condition Toleranca ia the aaximum p.rmi•••bl. variation of the .verage

••lua of the

....ure••nt fro. th••tand.rd or de.ir.d t.at condition. * T ••t Op.rating Tol.ranca i. the maxi.um p.rmi•••bl. variation of any m •••ure-

••nt. Wb.n .xpr•••ed a•• p.rc.nt.ga, th. maximum allowabla variation i. the .pacifi.d percant.ge of the .v.r.g. v.lue. 

# ..,

..,

Or
buring La

....ing**~tdoor** vat-bulb, OF

tnterine Le.ving

Extarnal ra.i.tanca to .ir flow, inches of v.tar
Elactric.l volt.g., : Tut Op.rating* Toleranc.

2.0 2.0

1.0 1.0

2.0 2.0

1.0 1.0

.05

'1.0 Te.t Conditionvv Toleranc•

0.5

0.5

0.3

.02 Iodoor dry-bulb, of Entering Leaving
IodoOT v.t-bulb, OF Entaring LuviDg
Outdoor dry-bulb, or Entariog Leaving
Outdoor v.t-bulb, OF Entering Leaving

txtamal re.i.tance to air-flow, inch•• of vatar
Electrical voltage, : 2.0

1.0

2.0

2.0

.05

2.0 0.5

0.5

l.0

.02



# ,. :II

N



## ..... - Teat Op.r.tinc Tolar.nca i. the ••xi.um per.i•••ble v.riation**~£** an1 me••ure-

••nt. Wh.n .xpr••••d a. a p.rtantag., the maximum .llow.bl. variation is**t~e** ap.cified p.rcantaca of tha averag. v.lu••

*- Teat Condition Tol.ranca ia tha .aximum permi••able variation of the aver••e value of the ••••ure.ent from the .t-and.rd or desired test condition. 

## en -t 

# ,. Z C 

# ,. :II 

### C
N 

### -. o I CD 

### -.N N 

## :a

6.2.3 TIIlI.C operat1D8 aad test condition tolerance. for frost acc:Jmulat1oD celt' 6.2.4**'lis~d.but1on** of fractional houn in temperature bin., h

..Urg load hours and outdoor duign temperature for the differant cl1JDAUc regLons 

## en ooot
Z C



## :a 

# c

Te.t Oplr.ting Tollr.nc. i. tb. aaximum plr.oiaa.bl. y.ri.tion of .ny me.aure- .nt. When expreued ••• perc.nt.g•• the

...ill1:1ll1 .llov.ble yari.tion i. the Ipecified percenuge of the avarag. valu.. Tut Operating Tolerailce**Duri~g** Heating .ppUu vh.n the heat pUlllp ia in the hutina mode. except for the Hrat 5 .inutu after t

.....ination of • defroat cycle. Test Operating Tol.rance During Defrolt .ppUaa duri"g • defrolt cycle and during til. firlt 5 .unutu after tbe terainatioD of a dafron cycle vhaD the hut pump ia operating in tbe beating aDd••
2 Tut Condition Tolera"c. ia thl maximwa permi

...bll yariation of the .verage value of the .uura

..."t frOll the auncl.rd or cluired teat conclition. Telt (ontlitioll Toluanc. appU

.. oal, 

# "".11 the beat pump ia operati". in the b

..tiD. _d••

, Ifot appl1cabl. dur1n& d.fro.t if the 1IIdoor fan 11 off

. Il.ctrical volug., :z: 2.0 Ent.ring 1. 5 Le.ving

External reli.tlnce to .i

....flov. incbu of v.ter .05 N



# .... o I CO



# ....

fI Pacllic: Coast Region 

# --- aegion I II III IV V VI Beating Load Bours, IlLIl 750 1250 1750 2250 2750 

## I 2750·

Outdoor Design Temperatur'l 

# I Too for the region 37 27 17 5 -10 30
Fractional Hours: B1II , T1 (oF)
J • 1 62 .291 .215 .153 .132 .106 .113 2 57 .239 .189 .142 .111 .092 

# I .206 3 52 .194 .163 .138 .103 .086 .215 4 47 .129 .143 .137 .093 .076 .204
5 42 .081 .112 .135 .100 .078 .141
6 37 .041 .088 .118 .109 .087 .076
7 32 .019 .056 .092 .126 .102 

# I .034
8 27 .005 .024 .047 .087 .094 .008 9 22 .001 .008 .021 .055 .074 .003 10 17 0 .002 .009 .036 .055 0 11 12 0 0 .005 .026 .047 0
12 7 0 0 .002 .013 .038 0 13 2 0 0 .001 .006 .029 0 14 -3 0 0 0 .002 .018 0
15 

### -e 0 0 0 .001 .010 0 16 -13 0 0 0 0 .005 0 17 -18 0 0 0 0 .002 0 18 -23 0 0 0 0 .001 0 .02 1.0 0.5

0.7 Tut Condition Tolerance(2)

(HeatIng Portion v::dyJ

4.0(3 )

10.0 2.0 2.0

1.0 Tuting Operating ToleranceO) DuTlng He.clDt Durlog DeTroIt

Enuring IA.Ying Enuring Le.Ying

Indoor vet-bulb. 

### ·r

Outdoor dew-point. ·F ladoor dry-bulb, 

### ·r

Ent.ring Le.Ying

Outdoor dry-bulb, 

### ·r



# ..... 

# -

## Regional Heating Load Hours

N W 

### 6.2.5



# VI

Region HL"g

I 750 II 1250 III 1750

IV 2250

V 2750 VI 2750 

## Actual heating load hours (ULHA ) and regional heating load hours**(ULH~** 

## for the United States



### 2500

This 

### map IS leasoniJlJlv acwlale tor 

### Illost paIlS of Ule Ulliled Stales but is necessarilv hl!Jhlv .ueneraltled. i11lj 

### cOllsequenl1v nOI 100 accurale in mounlalllous regIOns, pal1lcula/ti in Ihe 

### Rockies 

# IV

III

1500 

# II

Alaska Hawaii and

- Territories 3500 

## HLH 

# o HLH ):. 

## :u

t/) -t ):. Z 

## o ):. 

## :u 

# o
N



# .... o I 

### ex»



# ....

### ARI STANDARD 210-81



## 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



## 6.4 Ground Water Temperature Map (Reserved)

(FR Doc. 79-3a293 Filed 12-17-79; 8:45 am)
BILLING CODE**6450~1-C**



### 24