# 1992 STANDARD 

# for NTO 1cF 

## KHARY TCPC/E6%

A 

# II ABSORPTION WATER CHILLING AN]) WATERHEATING PACKAGES

4301 NORTH FAIRFAX DRIVE ARLINGTON, ViRGINIA 22203 

# PBPEBT1F 

# U.S.UVERNMENT• Pnce 22..oO PrtIC4IO U.S.A.

•

... 4.b ®Copyright 1992, by Air-Conditioning and Refngeration Institute Registered United States Patent and Trademark Office 

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. IMPORTANT SAFETY RECOMMENDATIONS It is strongly recommended that the system be designed, constructed, assembled and installed in accordance with nationally recognized safety requirements appropriate for systems covered by this standard. ARI, as a manufacturer’s trade association, uses its best efforts to develop standards, employing state-of-the-art and accepted industry practices. However, ARI does not certify or guarantee safety ofany products, components or systems designed, tested, rated, installed or operated in accordance with these standards or that any tests conducted under its standards will be non-hazardous or free fromrisk./

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# \\ TABLE OFkNTENTS RETURNTO ICF KH-LJBRARY TCPC/E6-13 SECTION PAGE Section 1. Purpose 1 Section 2. Scope 1 Section 3. Definitions 1 Section 4. Standard Equipment 3 Section 

### 5. Rating Requirement 4 Section 6. Voluntary Conformance 9 Tables and Figures Table 1. Part Load Conditions forRating 3 Figure 1. Allowable Tolerance Curve for Full and Part Load 10 Figure 2. IPLV and APLV Tolerance Curve 10 Appendix A Standard Requirements For Testing Absorption Water Chilling and Water Heating Packages Section Al. Purpose 11 SectionA2. Scope 11 Section A3. Definitions 11 Section A4. TestMethod 11 Section 

### A5. Instruments 12 Section A6. Measurements 12 Section A7. TestProcedure 14 Appendix B Derivation ofIntegrated PartLoad Values (IPLV and APLV) SectionBi. Purpose 18 Section B2. Scope 18 Section B3. Equation and Definition ofTerms 18 Figure Bi. Atlanta ASHRAE Weather Data Bin Hours

... • 20 Figure B2. Atlanta Office Building Cooling Operating Hours 21 Figure B3. Atlanta Office Building Cooling Load Profile 22 Figure B4. IPLV Bin Mechanical Cooling Hours 23 Table Bi. 

### Atlanta Office Building Summary 24


# PBIIPERTIF u.S. ERMTARI STANDARD 560-92 

## ABSORPTION WATER CHILLING AND WATER HEATING PACKAGES Section 1. Purpose 

### 1.1. Purpose. Thepurpose ofthis standard is to establish, for absorption water-chilling and water-heating packages; definitions, classifications, requirements for rating, and a description ofwhat constitutes standard equipment. 

### 1.1.1 Intent. This standard is intended for the guidance ofthe industry, including manufacturers, engineers, installers, contractors, and users. 1.2. Review. This standard is subjectto review and amendment as the technology advances. Section 2. Scope 2.1. Scope. This standard applies to single-effect steam and hot water operated water chilling units, double-effect steam and hot water operated water chilling units, and double-effectdirect-fired (natural gas, oil, LP gas) water chilling! heating units. Also included are multiple-effect and multi-loop cycle absorption water chiller/heating units. Wateris the refrigerant and LIBR (lithium bromide) the absorbent. See definitions in Section 3. 2.2 Exclusions. Notincluded in this standard are heatpump applications, exhaust gas fired applications, and nonproduct units especially constructed for field assembly for co-generation application. 

### Section 3. Definitions 

### 3.1 Absorption Water Chilling Package. A factory designed and prefabricated single-effectlow pressure steam or hot water operated assembly, or a double-effect high pressure steam operated dr hot water operated assembly not necessarily shipped as a singlepackage, consisting ofan evaporator, absorber, condenser, one or more generators, one or more solution heat exchangers, with interconnections and accessories, used for chilling water. 3.2 Absorption Water Chilling andHot WaterHeating Package. A factory designed and prefabricated double-effect direct-fired assembly, notnecessarily shipped as a single package. Consisting of an evaporator, absorber, condenser, two generators, one or more solution heat exchangers, with interconnections and accessories, used for chilling or heating water. Hot water may beprovided through a separate hotwaterheat exchanger to provide simultaneous heating and cooling operation. 3.3 CoefficientofPeiformance (COP). A ratio calculated by dividing the net cooling capacity by the heatinputrate, both expressedin consistentunits. 3.4 Single-EffectCycle. Dilute LIBR (lithium bromide) solution in the generator is concentrated when watervaporis boiled off. The watervaporis condensed in the condenser andreturned to the evaporator. The concentrated LIBR is returned to the absorberwhere it can absorb watervapor flashed offin the evaporator. 3.5 Double Effect Cycle. A high stage generator using highpressure steam, hot water, gas or oil as the energy means


### 1ARI STANDARD 560-92
releases low pressure watervapor which operates a low stage generator. Dilute LIBR solution in both low and high stage generators is concentrated when water vapor is boiled off. The watervapor is condensed in the condenserand returned to the evaporator. The concentrated LIBR is returned to the absorber where itcan absorb watervaporflashed offin the evaporator. 3.6 Fouling Factor. The thermal resistance due to fouling accumulated on the water side ofthe heattransfer surface. 3.6.1 FieldFouling Allowance. Provision for anticipated fouling during use. 3.7 HighPressureSteam. Steam pressures above 15 psig but below 150 psig. 3.8 LowPressure Steam. Steam pressures 15 psig and below. 3.9 NetCooling/Heating Capacity. The net cooling/heating capacityis considered as the usable capacity to the user’s system. 3.10 IntegratedPartLoadValue (IPLV). A single numberpart-load efficiency figure ofmeritcalculatedperthe conditions described in 5.1.4 referenced to Standard Rating Conditions. 3.11 ApplicationPartLoad Value (APLV). A single numberpart-load efficiency figure ofmerit calculated per the conditionsdescribed in 5.1.4 referenced to Selected Application Rating Conditions. 3.12 PublishedRating. A statementin the form ofcatalogs or computer output ofthe assigned values ofthoseperformance characteristics, under stated rating conditions, by which aunitmay be chosen to fitits application. These values apply to all units oflike nominal size and type (identification) produced by the same manufacturer. 3.12.1 StandardRating. A rating based on tests performed at Standard Rating Conditions. 312.2 ApplicationRating. A rating based on tests performed at applicationrating conditions (other than Standard Rating Conditions). 3.13 “Shall,” “Should,” “Recommended,” or “ItIs Recommended.” 3.13.1 Shall. Where “shall” or “shall not” is used for aprovision specified, thatprovision is mandatoryif compliancewith the standard is claimed. 3.13.2 Should, Recommended, orItis Recommended. “Should,” “Recommended,” or “ItIs Recommended” is used to indicate provisions which are not mandatory, but which are desirable as good practice. 3.14 WaterHeating Unit. Hot water can be provided from either ofthree circuits. 3.14.1 Through the evaporator circuit. 3.14.2 Through the absorbercondenser circuit. 3.14.3 Through a separate hot water heatexchanger. 

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2ARI STANDARD 560-92

Section 4. Standard Equipment 4.1 An absorption water chilling or water chilling-heating package shall include the following standard equipment: 1. Absorber 2. Condenser 3. Evaporator 4. Generator

- Low stage generator for single-effectunits and low and high stage generatorfor double-effect units. 5. Solution HeatExchangers 6. Pumps for solution and refrigerant recirculation 7. Controls
a. Low temperature cut-out b. Provisions forinterlocks to prevent or stop operation ofthe chillerpackage upon failure of chilled water flow. c. Means for electricallyprotecting pump motors included in the package againstthermal overload. Table 1. Part Load Conditions for Rating TPLV APLV Cooler (All Types) * 44 F [6.7°C] 100% load LWT 44 F [6.7°C] * Selected LWT

0% load LWT ** 2.4 gpm/ton Same as 100% load Flow rate (gpm) [0.043 L/s perkW] ** Selected gpni/ton Field fouling 0.00025

allowance (FFA) As specified Condenser

(Water-Cooled) 100% load EWT * 85 F [29.4°C] * Selected EWT

0% load EWT *** 60 F [15.6°C] *** 60 F [15.6°C] Flow rate (gpm) [L/S] ** Refer to Section 5.1 ** Selected gpm/ton [0.054 L/s perkW] [L/s perkWj 0.00025 FFA As specified Corrected forfield fouling allowance by using the calculation method described in A7.3 The flow rates (gpm) are to be held constant at full load values for allpart load conditions. Condenser entering fluid temperature varies linearly from 100% load values to 0% load values. LWT, leaving water (liquid) temperature. EWT, entering water (liquid) temperature. FFA, field fouling allowance in hr• ftF/Btu [m 2 • °C/W1

3ARI STANDARD 560-92
d. Chilled water/heating temperature controller. e. Instrumentpanel. f. Burner controls and gas/oil train safeties per U.L. Standards 795 Commercial-Industrial GasHeating Equipment and 726 011 forDirect-Fired Water ChillingHeating Units. 8. Miscellaneous
a. Absorbent charge. b. Means forremoval ofnon condensables from chiller. c. Installation and operating instructions. d. Nameplate. Section 5. Rating Requirement 5.1 PublishedRatings. Published ratings consist ofStandard Ratings and application ratings, whetherpublished in catalogs or as computer output. 5.1.1 StandardRatings. All Standard Ratings shall be expressed in tons [kW] ofrefrigeration for water chilling units and Btuh [kW] for water heating and direct-fired chiller/heaters and shall be at the following Standard Rating Conditions: Leaving chilled-watertemperature

- 44 F [6.7°C] Entering absorber/condenser (cooling) watertemperature

- 85 F [29.4°C] Absorber/condenser water side field fouling allowance

- 0.00025 hr sq ft F/Thai [0.000044 m 2 • °C/W] Cooler (evaporator) water-side field fouling allowance

- 0.00025 hr sq ft FfBtu [0.000044 m 2 °C/W] Heating (hot water) water-side field fouling allowance

- 0.00025 hr sq ft F/Btu [0.000044 m 2 • °C/W] Chilled water evaporator circuitflow rate

- 2.4 gpm/ton [0.43 L/s perkWj Absorber/condenser waterflow rate, single effect

- 3.6 gpm/ton [.065 L/s per kWj Absorber/condenser waterflow rate, double effect

- 4.0 gpm [.072 L/s per kW] Absorber/condenser waterflow rate, double effectdirect-fired

- 4.5 gpm/ton, [.081 L/s perkW] Heating waterflowrate

- Manufacturer’s Choice Heating water entering temperature

- 130 F [54.4°C] Leaving temperature

- 140 F [60.0°C] Entering gas pressure at burnerinlet gas pressure specified based on type oftest gas as defined in Tables VII and Vifi of Gas-Fired CentralFurnaces (except Direct Vent CentralFurnaces) ANSI Z21.47-1989. Entering oil

- Manufacturer’s Choice Heating Value ofFuel

- value to be specified in ratings and mustbe the higher heating value. Heating Value

- No 2 oil

- 140,000 Btu/gal. [38,971 KJ/L] 5.1.2 ApplicationRatings. It is .)

4ART STANDARD 560-92 recommended that application ratings (ratings determined at other than Standard Rating Conditions) include ratings at the following range of conditions: Leaving chilled water temperature

- 40 to 48 F (increments 2 F or less) [4.4 to 8.9 °C, increments 1°C or less] Entering condensing (cooling) water

- 80 to 90 F (increments 5 F or less) [26.7 to 32.2 °C, increments 3 °C or less] Condensing (cooling) and absorber water flow rate limit

- 2.8 to 4.5 gpm/ton [0.05 to 0.081 L/s kW] Heating water flow rate (double effect heating cycle)

- manufacturer’s standard gprn/ton [L/s kW] Steam pressure (at steam inlet header single stage unit)

- 0 to 12 psig (increments 2 psi or less)

- [0 to 82.7 kPa gauge, increments 14 kPa or less] Steam pressure (at steam gauge, inlet header high stage generator)

- Manufacturer’s standard (increments 15 psi or less) Entering hot water temperature for hot water operated units

- 240 to 400 F [115 to 204°C] 5.1.2.1 FieldFouling Allowance. When application ratings are published, they shall include those with field fouling allowance as specified in 5.1.1. Additional application ratings, or means of determining these ratings, at other fouling allowances may also be published (see 5.2). 5.1.3 Determination ofRatings. Published ratings shall be determined from testresults in accordance with the following:
a. Evaporator, condenser, absorber, and hot water heat exchanger water-side transfer surfaces shall be considered clean for testing. Test will be assumed to reflect a fouling factor of0.0000 hr sq ft FfBtu [0.0000m 2 C/WJ. b. To determine published rating at any field allowance from test data at a fouling factor of0.0000 hr ft FfBtu [0.0000 m 2 C/W] the calculations for fouling adjustments described in Appendix A shall be used. 5.1.4 PartLoadRatings. Part load ratings ofan absorption water-chilling package, when presented as typical, shall be calculated on the basis that:
a. Leaving chilled water temperature V remains constant at the full load rating value. b. Leaving heating water temperature remains constant at the full load rating value.
c. Chilled evaporator water flow rate remains constant atthe full loadrating value. d. Entering absorber/condenser water temperature varies linearly with load, decreasing from the value atthe rating condition to 60 F [15.6°C] or minimum acceptable temperature at zero load, whichever is greater.

5ART STANDARD 560-92

e. Condenser and absorber water flow rate remains constant at the full loadrated value. f. Cooler and condenser field fouling allowanceremain constant at the full loadrated value. g. Heating waterflow rate remains constant atthe same full load rated value. 5.1.4.1 Part loadperformance ofan absorption water-chilling package may be presented in three ways:

a. Integrated PartLoad Value (IPLV) which is based on a Standard Rating Condition. b. Application PartLoad Value (APLV) which is based on a Selected Application Rating Condition.
•c. Separate part load datapoint(s). 5.1.4.2 IPLV and APLV values shall be determined by test at the conditions prescribed in 5.1.4. 5.1.4.3 For water-chilling packages covered by this standard, part load values (IPLV or APLV) shall be calculated as follows:

a. Determine the COP at 100 percent; 75 percent, 50 percent and 25 percentload points at the conditions specified in 5.1.4. b. Use the following equation to calculate IPLV or APLV: IPLV or APLV = .17A+.39B+.33C+.11.D (1) where A=CO.P at 100% .B=COP at 75% COP at 50%

- D=COP at 25% For derivation ofequation (1), see Appendix B. 5.1.4.4 Ifthe package cannot be operated at the 25% load point, operate it at minimum capacity with the condenser entering water (liquid) temperature (EWT) corresponding to 25% capacity conditions. Then calculate COP at the measured kW divided by 25% ofthe 100% load• capacity obtained by test. 5.1.5 Minimum PublishedRating Data. Minimumpublished rating data shall include package designation(s), including pass or baffle arrangements and rated water flow in gpm [L/sJ. Each package shall be rated atthe Standard Rating conditions and at any additional application rating conditions selected, and the rating at any condition shall include:
a. Capacity, tons ofrefrigeration [kW] and/or heat output, MBH [kcal/hr]. b. Steam inputrequirement (pressure and flow rate) or equivalent hot water requirements (entering temperature, temperature difference, and water flow rate).

6ART STANDARD 560-92

c. Leaving chified water temperature, F [°CJ. d. Entering condensing (cooling) watertemperature, F [°Cj.
e. Evaporator (cooler) water pressure drop (inletto outlet), psi or ft ofwater [kPa]. f. Absorber/condenser (cooling) waterpressure drop (inletto outlet), psi or ft ofwater [kPa] including the cross connecting piping. g. Hot waterpressure drop through generator (concentrator), psi or ft ofwater [kPa}. h. Statement offouling factor allowances on absorber/condenser (cooling) water-side, evaporator (cooler) water-side; and on heating water-side (direct-fired units) i. Leaving heating water temperature, F [°C] (Direct-fired units). 

## j. Heating value ofgas, Btu/ft 3 [kcal/m 3 J (Direct-fired units). k. Heating value ofoil, Btu/gal {kcal/L] (Direct-firedunits). 1. Consumption rate for gas, MBH [m 3 /hr} (Direct-fired units).
m. Consumption rate for oil, GPH {L/hr] (Direct-fired units).
n. Average electrical power consumption for all auxiliary components including solution and refrigerantpumps, purge, control panel, burnerfan, burner controls, etc. Powerrequired by system water pumps shall be excluded. 5.2 Water-Side Fouling.

5.2.1 Fouling atStandardRating Conditions. The choice ofa field fouling allowance of 0.00025 hr sq ft F/Btu [.000044m 2 °CiW] for evaporators and condensers for the Standard Rating Condition is the basis forpublished rating conditions (see 5.1.1 and 5.1.2.1) and which provide the selections which anticipate the effect of typical fouling in evaporators and absorber/condenser (cooling) water circuits. Fouling tends to reduce capacity and increase energy consumption. An application will remain wfthin the limits ofthe field fouling allowance ifacceptable water quality is maintained by treatment, and the heat exchanger surfaces are periodically cleaned. 5.2.2 Additional Fouling. Conditions such as water hardness, organic material, suspended solids and/orwater velocity
• may necessitate the use ofa greater field
• fouling allowance than thatprovided in the Standard Rating ofequipment. 5.2.3 Adjust,nentsforAdditional Fouling. Published ratings may include the effects ofadditional field fouling allowance. Suàh ratings shall be determined by using the method described in paragraph 5.l.3b. 5.3 Verification ofCapacity andPower Requirements. Where verification of capacity and powerrequirements is required, it shall be by test in accordance

7ART STANDARD 560-92
with the method set forth in Appendix A to this standard. 5.4 Publication ofRatings. Wherever applicationratings are published orprinted, they shall include, or be accompanied by, the Standard Rating, clearly designated as such, and shall include a statement ofthe conditions atwhich the ratings apply. 5.5 Tolerances.

5.5.1 Allowable Tolerance. The allowable test tolerance on capacity (tons) [kW], COP, and heat balance shall be determined from the following equation: Tolerance in percenttons {kWj, COP orpercentheat balance (U.S. Standard Units DT in F.) =lO.5%-(0.07x%FL)+ (1500/(DT x % FL)) [SI units DT) in °C]

= 10.5%

- (0.07 x % FL) + (833.3tDT x % FL)) Where FL = Full Load DT = Difference between entering and leaving chilled water temperature at full load, F [°C]. See Figure 1. Allowable Tolerance Curves for Full and PartLoad for graphical representation only. 5.5.2 FullLoad. Published ARTratings shall be such that any production package shall, upon testhave a full load capacity not less than 100 percent ofits rated capacity less the allowable tolerance and a full load COP not less than 100 percent ofits rated COP minus the allowable tolerance. The allowable tolerance shall be determined by the equation specified in 5.5.1. Waterpressure drop in the cooler absorber and absorber/condenser shall not exceed 115 percent ofrated pressure drop atrated gpm, [L/s} in those vessels. The tested total auxiliarypower shall be no more than 5% ofthe rated auxiliary power. Example (Full load): (in U.S. Standard Units only forclarity) Rated Full Load Performance Rated capacity = 100 tons Rated heatinput = 1237 MBH Cooling DT = IOF 

## COP=boo X12,000.. 097 1,237,000 Allowable TestPerformance: Tolerance = 10.5

- (.07 x 100) +

(1500) (lOx l00)=10.5-7÷1.5=5% Min. allowable capacity = (100 -5) x 100

= 95 tons Mm. allowable COP = (100

- 5) x .97 = 0.92 100 Max. heatinput atmm. capacity =

95 tons x 12,000 = 1239 MBH .92 COP 1,000 5.5.3 PartLoad. The tolerance on part load power COP shall be the tolerance 

# e

e

8ARI STANDARD 560-92
for COP determined by the equation equation: specified in 5.5.1. Allowable Tolerance (percent) Example (Part Load) (in U.S. Standard 

### = 6.5 + 35tDT DT in F Units only for clarify) 

### [= 6.5 + 19.4/DTJ DT in °C Rated Part Load Performance DT as specified in 5.5.1 50% capacity 

### = 50 tons See Figure 2. IPLV and APLV Tolerance 50% heatrate 

### = 700 MBH Curve for graphical representation only. COP =0.86 Full Load DTp.r 

### = 1OF The single number IPLV and APLV, calculated for the part load conditions Allowable TestPerformance: which apply, shall not exceed the rated IPLV or APLV by more than the Tolerance 

### = 10.5

- (.07 x 50) + (1500) allowed tolerance. (10 x 50)


### = 10.5

- 3.5 + 3 

### = 10% Section 6. Volimtary Conformance Mm. allowable COP 

### = (100-10) x 0.86 6.1 Conformance. While conformance 100 with this standard is voluntary,


### = 0.82 conformance shall not be claimed or implied forproducts or equipmentwithin 5.5.4 IPLVAND APLVTolerance. The its Purpose (Section 1) and Scope (Section allowable tolerance on IPLV and APLV 2) unless such claims meet all the shall be determined by the following requirements ofthe Standard.



### 9ART STANDARD 560-92

I— z w 30 w a w C.) z a: Iii -J 0 I—

15

16 [4

10 z a: 8 w -J 0
‘ 6 4. 2 Figure 1. AllowableTolerance Curves ForFull And Part Load

DT (SEE 5.5.1)

Figure 2. LPLV and APLV Tolerance Curve PERCENT FULL LOAD

01 2 34 5 67 8 9101112
DT 1
. (SEE 5.5.1) COOLER DTFLAT FULL LOAD. F

10

### ARI STANDARD 560-92 Appendix A: Standard Requirements for Testing Absorption Water Chilling and Water Heating Packages Section Al. Purpose Al.l Purpose. The purpose ofthis appendix is to prescribe a method of testing absorption waterchilling and water heating packages to verify capacity and heat energy requirements at a specific set ofconditions. Itis intended thatthis testing will occur where instrumentation and load stability can beprovided. It is notthe intent ofthis standard to provide fortesting in typical field installations where steady state conditions are often difficultto achieve andprovisions for measurement are not made. Section A2. Scope A2.l Scope. This appendix applies to absorption water chillingpackages used to chill or heatwater, as defined in Section 3 ofthis standard. Section A3. Definitions A3.l Definitions. Definitions ofthis appendix are identical with those in Section 3 ofthis standard. Section A4. Test

### Method A4.1 TestMethod. A4.1.l The testwill measure net cooling capacity (tons ofrefrigeration) [kWj or netheating capacity (MBH of heating) [kW] and heat energy input requirements, at a specific set of conditions. A4.l.2 After steady-state conditions have been established at the specific set ofconditions and within the tolerance setforth in A7.2, three sets ofdata shall be taken, at aminimum of 5-minute intervals. To minimize the effects oftransient conditions, test readings should be taken as simultaneously as possible. A4.1.3 The test shall include a measurement ofthe net heatremoved from the water as itpasses through the chilled water or heating water circuit by determination ofthe following:
a. Waterflow rate. b. Temperature difference between entering and leaving water. A4.l.4 The heatremoved from the chilled water is equal to the product of the chilled water orheating water flow rate, the water temperature difference, the specific heat ofwater, and the specific gravity ofthe water. A4.1.5 The test shall include the determination ofthe absorption chilling and waterheating package heatinput energy. This heat energy shall be determined by a measurement as outlined in the testprocedure (see A7). A4.l.6 In addition to the determination ofnetheatremoved and heat energy inputrequired, data shall be taken to prepare aheat balance to substantiate the validity ofthe test. A4.2 Conditions ofHeatTransfer Surfaces.

11ARI STANDARD 560-92
A4.2.1 Tests conducted in accordance with this standard may require cleaning (in accordance with manufacturer’s instructions) ofthe heattransfer surfaces. The “as-tested 11 water-side fouling factors shall then be assumed to be 0.000 hr sq ftF/Btu [0.0000m 2 . °C/WJ.

Section AS. Instruments A5.1 Instruments shall be selected from the types listed in ASHRAE Standard 14- 80 Methods ofTesting forRating Positive Displacement Condensing Units (American Society ofHeating, Refrigerating and AirConditioning Engineers, Inc.). A5.L1 Accuracy ofinstruments selected shall be in accordance with that specified in ASHRAE Standard 14-80. A5.l.2 Temperature measurements shall be made in accordance with ASHRAE Standard 41-86 Standard MethodforTemperature Measurement (American Society ofHeating, Refrigerating and Air-Conditioning Engineers, Inc.). A5.1.3 Flowmeters shall be constructed and installed in accordance with the applicableportion ofthe latest edition ASME FluidMeters--Their Theory andApplications. Turbine flow meters may also be used in accordance with Instrument Society ofAmerica Standard ISA RP31.1977 Specflcation, Installation, and Calibration ofTurbine FlowMeters. A5.1.4 Electrical instruments scales should be such thatreadings will be at least one-halfoffull scale deflection, and other instruments, such as gages and thermometers should be calibrated over the range oftestreadings. A5.l.5 Flow meters for the measurement offuel gas shall conform to one ofthe three following standards; ANSI B109.l-1986, Diaphragm Type Gas DisplacementMeters (500 Cubic FootperHour Capacity and Under), ANSI B109.2-1986, Diaphragm Type Gas DisplacementMeters (Over500 CubicFeetperHour Capacity), and ANSI Bl09.3-1986, Rotary Type Gas DisplacementMeters. Flow meters for fuel oil should be timed weight orthe timed volume method when instruments should be traced to the American Society ofMechanical Engineers (ASME). A5.1.6 Steam mass flow measurement should be done by measuring steam condensate flow. Ifcondensate flow is measured in an open tank, then a condensate cooler is recommended to prevent flashing. Section A6. Measurements A6.l Data to be recorded after steadystate conditions have been established: A6.1.1 TestData
a. Temperature ofwater entering cooler (evaporator), F [°C]. b. Temperature ofwater leaving cooler (evaporator), F [°CJ. c. Temperature ofwater entering absorberF [°CJ. d. Temperature ofwater leaving condenser, F [°CJ. e. Temperature ofwater entering absorber/condenserifapplicable (heating cycle) F [°Cj. 

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12

### ART STANDARD 560-92
f. Temperature ofwater leaving absorber/condenser ifapplicable (heating cycle) F [°C]. g. Cooler (evaporator) water flow rate, gpm or lb/hr [L/s]. h. Absorber/condenserflow rate, gpm or lb/hr [L/sj. i. HeatEnergy Input from one of the following: 1. Steam consumption, lb/hr [kg/si. Steam supply pressure, psig [kPa]. Steam supply temperature, F [°CJ. Steam condensate temperature, F [°CJ. 2. Hot water flow rate, gpm [Us]. Hot water supply temperature, F [°C]. Hot waterleaving temperature, F [°C]. 3. Gas consumption, ft 3 /hr [M 3 /hrj. Higher gas heating value (HHV), BtuIFt 3 [J/M 3 ]. Gas pressure entering gas train, in. 1120 orpsig [mm AqJ. 4. Oil consumption, gph L/s. Higher oil heating value (HHV), Btu/gal [JIL]. Oil classification (for example, Class A Heavy Oil). 

## j. Electrical power consumption for components, kW [kW]. k. Temperature ofwater entering heating circuit, F [°C]. (Direct fired heating units.) Temperature ofwater leaving heating circuit, F [°C]. (Directfiredheating units.) m. Flow rate ofhot water, gpm, [L/sJ. (Direct-fired heating units.) A6.1.2 ifchilled wateris used for some incidental functional use, the temperature and flow measurements of chilled water must be made atpoints beyond such take-offs and returns, so that the measured rise reflects net cooling capacity. A6.1.3 Ifabsorber/condenserwater is used for some incidental use, the temperature and flow measurements of condensing water must be made at points ahead ofsuch take-offs and returns, so thatthe measuredrise reflects gross condensing heatrejection. A6.1.4 ifsteamcondensate is used for some incidental functional use, the heat contentused must be added to the heat inputfor heatbalance purposes. A6.2 Auxiliary data to be recorded.for general information. A6.2.1 Nameplate data, including make and model, sufficient to completely identify the water-chilling package. A6.2.2 Evaporator (cooler) water pressure drop (inletto outlet), psi or ft ofwater [kPaj. A6.2..3 Absorber/condenser water pressure drop (inletto outlet), psi or ft ofwater [kPa]. A6.2.4 Heating waterpressure drop (inletto outlet) psi orft ofwater [kPa]. A6.2.5 Ambient temperature at test site, F {°. A6..3 RecordData 

### A6.3.1 Date, place and time oftest.



### 13ART STANDARD 560-92
A6.3.2 Name oftest supervisor and witnessing personnel. Section A7. TestProcedure A7.1 PreparationforTest A7.1.1 The absorption water-chilling package, which has been completely installed in accordance with the manufacturer’s instructions and is ready fornormal operation, shall be provided with the necessary instruments. A7.1.2 The test shall notbe started until non-condensables have been removed from the system. A71.3 Atthe manufacturer’s option, tubes in the absorber, condenser, evaporator, and separate heat exchanger (ifused for heating) may be cleaned as provided in A4.2. A7.2 Operation andLimits

14A7.2.1 Start the system and establish the testing conditions in accordance with the following tolerances and instructions:
a. Individual readings ofwater temperature leaving the evaporator (cooler) shall not vary from the specified values by more than 0.5 F [0.3°C]. Individual readings entering the absorber/condenserwatercircuit shall notvary by more than 0.5 F (0.3°C). Individualreadings leaving the hot water (heating) exchanger shall notvary by more than 0.5 F [0.3°C]. Care mustbe taken so thatthese water temperatures are the average bulk stream temperatures. b. The chilled water, cooling water, andheating waterflow rates (ifapplicable) shall not deviate more than ± 5 percent fromthat specified. c. The leaving chilled water. temperature shall be decreased by an incrementcalculated per A7.3 corresponding to the specifiedfield fouling allowance. d. The entering absorber water temperature shall be increased by an increment calculated per A7.3 corresponding to the specified field fouling allowance. e. The leaving hotwater temperature shall be increased by an incrementcalculated per A7.3 corresponding to the specified field fouling allowance. (Direct-fired heating units) f. Steam supplypressure shall be maintained within ±0.2 psig [1.4 kPa] ofthe specffied pressure and shall be furnished dry or within the superheat range specified by the chiller manufacturer. g. Gas heating values to be used fortesting are specified in ANSI Z21.47 Furnaces, GasFired Central (exceptDirect Vent CentralFurnaces). Flue gas backpressure shall be maintained within range specified by the manufacturer. h. Hot water supply temperature to single-stage generators shall be maintained within ± 5 F [± 3°C] ofthe specified temperature and the hot water 

# o

9)ARI STANDARD 560-92
flow rate shall be maintained within ± 5 percent ofthe specified flow rate. i. Electric motors furnished as part ofthe chillerpackage shall be supplied with nameplate voltage and frequency at the motorterminals. 

## j. For direct-fired absorption chiller- heaters, the CO value in the combustion gas analysis is specified as less than 0.02%. When oil is used as an energy source, the smoke density measured by calorimetric filter paper, is specified as No. 3 or below. A7.3 

### MethodforSimulating FieldFouling Allowance atFull andPartLoad Conditions A7.3.1 Obtain the log mean temperature difference (LMTD) for the cooler and/or absorber/condenserusing the following equation atthe specified field fouling allowance (ff). Due to the complexity ofanalyzing the fouling effect in the condenser and absorber separately, the two heat exchangers have been combined in an approximate calculation for convenience. LMT.D R (Al) in (1 + R/S) A7.32 Derivation ofLMTD: LJYITD (ts

# — t 9 ) 

# — (t 3

# — t 1 ) in

— twi The Incremental LMTD (ILMTD) is determined using the following equations: ILM’ID = ff 8

# (-i) (A2)
A7.3.3 The water temperature difference TDa needed to simulate the additional fouling, TDa can be calculated: TDa = 

# - S, (A3a)



## zv=se-1 (A3b)

Where: S 5 , = small temperature difference as specified S, = small temperature difference as tested in cleaned condition The water temperature difference, TDa is then added to the absorber/condenser entering water temperature or subtracted from the cooler leaving water temperature to simulate the additional fouling factor. A7.3.4 Example-Absorber/Condenser FoulingInside Tubes (in U.S. Standard (t 

# —

— t 1 ) tg t 9 )

+ (t 1 

# — t 9 )



# — twi

Where: R

- LMTJJ

# - ILMTD
R c ez_1

15

### AM STANDARD 560-92
units only,for clarity), 

## m 6 =

— Specified field fouling allowance if, = 0.00025 hr sq ftF/Btu 6 SP ez_1 Absorber/condenserload, q = 13,000,000 Btuh Absorber/condenserleaving water R temp,t 1 - 

### [

. C] LMTD-ILMTD Specified absorber/condenser entering water temp. t = 85F [29.4°C] TDa=5.0 3.25 Absorber/condenserinside* tube = 1.75F surface area, A = 1500 sq ft [139.4M 2 ]
* (Since fouling is inside tubes in this example) The entering absorber/condenser water temperature for testing is then raised Saturated condensing temperature 1.92 F to simulate the field fouling allowance of0.00025 hr sq ftFfBtu.

= 106F [41.0°C] The entering condenser water S,, t,

- ti 106

- 101 5F temperature will be 85 + 1.75 or 86.8 R=t 1 -t=101-85=16F F.

= in (1 ÷ R/S 

### ) A7.3.5 Symbols and Subscripts. The symbols and subscripts used in Equations Al through A3b are as follows:

= in 1616/5) = 11

. 15 A = Total heat transfer surface, sq ft [mj for cooler or absorber and condenser ff, 1 , = 0.00025 hr. sq. ft. F/Btu A = A 1 forfouling inside tubes A = A 0 forfouling outside tubes ILI4TD = ff

# I ..c

‘ (A2) e = Base fornatural logarithm A 1 q = Total heatrejectionrate or netrefrigerantcapacity of cooler, Btuh [Wj 0. 00025 

# ( 13, 000, 000 R = Water temperature range = 1, 500 

### / absolute value (t,

- t) S, = Small temperature difference as specified

= 2 .16F t = Temperature, F [°C] ff, = Specified field fouling allowance



### 16.ARI STANDARD 560-92 Subscripts:
a = additional fouling e = entering c cleaned f = fouled or fouling i =inside o = outside 1 = leaving s = saturatedvapor w = water sp = specified A7.4 HeatBalance

- Substantiating Test A7.4.1 Basic. TotalHeatIn-Total Heat Out. In most cases for singleeffect absorption units, heatlosses or heat gain caused by radiation, convection, etc., are relatively small and may not be considered in the overall heat balance, but may be compensated forin the heat balance closure allowance (see A7.4.3). A7.4.2 For double-effectmachines the high stage generator heatloss may be significantfor an uninsulated surface. Since this surface is normally insulated on thejob site, the heat loss due to an uninsulated high stage generator surface can be subtracted from the measured value. The heat loss can be determined by radiant heat transfer equations or verification by tests. A7.4.3 Omission ofthe small heat losses and gains mentioned in A7.4.1 results in a heatbalance equation as follows: HB hS’1 9 VC

100 DC where:

= input from heat source

= net cooling capacity

= heatreject to condensing circuit Any consistent system ofheat units may be used in the above equation. For any test ofa liquid cooled chiller to be acceptable, the heat balance (percent) shall be within the allowable tolerance calculated per 5.5.1 forthe applicable conditions. ev

q

17ARI STANDARD 560-92 

### APPENDIX B DERIVATION OF INTEGRATED PART LOAD VALUES (IPLY 

### AN]) APLV)

Section Bi. Purpose B1.l Purpose. This appendL is intended to show the derivation and an example ofthe calculation of theIntegratedPartLoadValue(IPLV) orApplication PartLoad Value (APLV). Section B2. Scope B2.l Scope. This appendixis forequipmentcovered by this standard. Thebasic equations andprocedures are intended to provide a consistent procedure for calculating a single number part load performance number for water chilling products. Thebasic equations (la) and (ib) asshown in section B3.1 were developed based on a typical office building located in Atlanta. The weather data used forthisbuilding wasobtainedfromASHRAEweather dataforthe city ofAtlanta. A typical officebuilding profile was assumed with 2125 hours ofmechanical cooling per year, which was determined based on operation from 7 a.m. to 6p.m. 5 days perweek, and from 7 a.m. to 1 p.m. on Saturdays. The building was equipped with an air side economizer. A single chillerwas used forthis building and was sized to be atfullcapacityatthedesign fullloadconditions. The design conditions for the building are; SummerDesign Dry Bulb Temperature 94 F SummerDesign Wet Bulb Temperature 74 F Zero Load Dry Bulb Temperature 35 F Thebuilding load was assumed to vaiy linearly with the ambienttemperature. Thedetails forthebuilding aresummarizedinFigures Bi to BA and in Table Bi. It should be stressed that the equation derived from the above data is intended to be a typical building model,butbecauseofwide variationsactualbuildings we strong recommend that actual energy analysis be used to determine the part load performance and energy use for the chiller and building. The following are some items that can affect the chiller operation atpartload;

• AmbientTemperatureProfile

• Building LoadProffle

• Water Temperature Setpoints
• Cooling Tower Size and Control

• Number ofChillers
• Control ofchillers For example, the fourIPLV weighing factors forthe same building in Atlantawith two chillers vs the one chiller wouldbe: CHILLER WEIGHING FACTOR LOAD 1 CHILLER 2 CHILLERS 100% 0.17 0.29 75% 0.39 0.50 50% 0.33 0.21 25% 0.11 0.0

Section B3. Equation and Definition ofTerms B3.1 General Equation The following equation should be used when the efficiency is expressed in capacity divided by unitinputpower. An efficiency expressed as COP should use this equation.

LPLV

or = O.17A + O.39B + O.33C + 0.11D (1) APLV
where: A = COP at 100% capacity B = COP at 75% capacity C = COP at 50% capacity D = COP at 25% capacity The IPLV and APLV rating requires that the unit efficiency be determined at 100%, 75%, 50% and


### 18AR! STANDARD 560-92

25% attheconditions as specifiedinTableBi. Ifthe CHILLER PERFORMANCE DATA unitcannotbeoperatedatthe25% capacitypoint, the 25% point should be determined with the entering % LOAD CAPACiTY INPUT absorber/condenser entering water (liquid) fluid (Tons) (MBtuh) temperature corresponding to the 25% capacity conditions. The efficiency should be calculated by 100% 400 685 using the measured power at these conditions and 75% 300 600 25% ofthe full load capacity. 50% 200 400 33%* 132 330 133.2 Equation Constants The constants 0.17, 0.39, * Minimum possible unit capacity 0.33, and0.25 arebasedonthetypicalofficebuilding in Atlanta. To reduce the number ofmachine data Using theabovedatathepartloadkw/ton values can points theASNRAEbasedbin data was reducedto4 be calculated. bins as shown below; POINT LOAD CAP INPUT COP BIN LOAD RANGE (TONS) (MBtuh)
1 100%-75% A 100% 400 685 0.70 2 75%-50% B 75% 300 600 0.60 3 50%-25% C 50% 200 400 0.50 4 25%-0% D 25% 100 330 0.40 Using the ASHRAE data for mechanical cooling JPLV = 0.17 x 0.70 + 0.39 x 0.60 + 0.33 x 0.50 hours of operation and the average chiller + 0.11 x0.40 = 0.59 COP performance for the load bin the following equation can be used to calculate a weighted part load performancerating.

LPLV A B B C

or = O.3421x + + 0.431tx • + A.PLV 2 2

+ D) + 0.OOx(D)
The above equation can be siinpliliedby eliminating the division by 2 which results in the following equation;

LPLV

or = 0.17A + 0.39.8 + 0.33C + 0.11D (1) APLV
B3.3 Sample Calculation The following is an example ofakw/ton IPLV based calculation;

19ARI STANDARD 

### 560-92

20 

## ATLANTA 

## ASHRAE WEATHER DATA BIN HOURS FIGURE Bi

U, 0 

# = z 1,400 TOTAL HOURS

— 8760 HRS 1,201 1,200 

# 1 986] 846 800 709 666

— 608 600 1 400 305 200 .1.3.5.] 

# oiI 

# II 0

- - - - a a e a e a a e a a a
•

- Cd Cl in in a a i— a a a • • I I I I I I I I I I I o in 0 10 0 10 0 10 0 10 0 10 0 10 0 10 0
,.- (14 (14 t q io II) in€D

- a a a OUTSIDE AIR TEMPERATURE BIN (F) 811____________________________________
ART STANDARD 560-92

ATLANTA OFFICE BUILDING COOLING OPERATING HOURS

400

00
U, 2 9 200

100 FIGURE 82

QJTSIOE AIR TBdPERATUR BIN () 0 hEQIANICAL CLI oiz ctOLIG 0
, 1• ci ci ci ci r. ci ci ci (•1 c,I 1• 1 C., Ui Ifl W Ia ci ci ci

21ARI STANDARD 560-92 _________________________________

ATLANTA OFFICE BUILDING COOLING LOAD PROFILE FIGURE 63

120.0

100.0

eo .0
‘-I
60.0

40.0

20.0

MECI-ANICAL COOL FG COOLING

0.0 m ‘ UI UI 1- Ui UI Ci 1 UI 1 cJ c..I Ii O Ifl CD CD I 1 Ci Ci Ci
I I I I I I I I I I I I I I I I Ifl D U C In C In C Wi C Ifl C In C

— (V (V fl Ci 1 1 In In CU ID ? I CD CD UI OUTSIDE AIR T9.4PERATUR 61N CP)

22ART STANDARD 560-92

4 

# I
IPLV BIN MECHANICAL COOLING HOURS FIGURE 84 TOTAL OPERATING HOURS = 2125 HRS 1,200.0
43.1% 1,000.0 916.0

800.0
600.0 22%

-
400.0

200.0

0.0 0-25% OUTSIDE AIR TEMPERATURE BIN (9 25-50% 50-75% 75-100%

23ARI STANDARD 560-92

TABLE Bi. ATLANTA OFFICE BUILDING SUMMARY
OUTSIDE AVGDB. TOTALBiN TOTAL COOLING 0-25% BIN 25-50% BIN 50-75% BIN 75-100% BiN

TEMP. HOURS COOLING LOAD (%) HOURS HOURS HOURS HOURS

(F) (F) HOURS 100-105 102.5 0 0 100.00 0 0 0 0
95-99 97.5 0 0 100.00 0 0 0 0
90-94 92.5 156 103 M 97.56 0 0 0 103
85-89 87.5 367 254 M 88.96 0 0 0 254
80-84 82.5 611 370 M 80.51 0 0 0 370
75-79 77.5 838 353 M 72.03 0 0 353 0
70-74 72.5 1201 301 M 63.56 0 0 301 0
65-69 67.5 986 262 M 55.08 0 0 262 0
60-64 62.5 846 248 M 46.61 0 248 0 0
55-59 57.5 773 234 M 38.14 0 234 0 0
50-54 52.5 709 213 E 29.66 0 0 0 0
45-49 47.5 666 200 E 21.19 0 0 0 0
40-44 42.5 608 158 E 12.71 0 0 0 0
35-39 37.5 471 108 E 4.24 0 0 0 0
30-34 32.5 305 0 0 0 0 0 0
25-29 27.5 135 0 0 0 0 0 0
20-24 22.5 53 0 0 0 0 0 0
15-19 17.5 35 0 0 0 0 0 0
10-14 12.5 0 0 0 0 0 0 0 TOTAL 8760 2125M 0 482 M 916 M 727 M
% TOTAL 0 22.68% 43.11% 34.21%

E

- Economizeroperation M

- Mechanical refrigeration cooling

24