TEST REPORT #7 System Drop-In Tests of R134a Alternative ......Low GWP AREP R134a W/C Screw Chiller...

Air-Conditioning, Heating, and Refrigeration Institute (AHRI) Low-GWP Alternative Refrigerants Evaluation Program (Low-GWP AREP) TEST REPORT #7 System Drop-In Tests of R134a Alternative Refrigerants (ARM-42a, N-13a, N-13b, R-1234ze(E), and OpteonTM XP10) in a 230-RT Water-Cooled Water Chiller Ken Schultz Steve Kujak Trane / Ingersoll Rand 3600 Pammel Creek Rd La Crosse, WI 54601 January 25, 2013 This report has been made available to the public as part of the author company’s participation in the AHRI’s Low-GWP AREP.

List of Tested Refrigerants’ Compositions (Mass%)

ARM-42a R-134a/R-152a/R-1234yf (7/11/82) N-13a R-134a/R-1234yf/R-1234ze(E) (42/18/40) N-13b R-134a/R-1234ze(E) (42/58) R-1234ze(E) R-1234ze(E) (100) OpteonTM XP10 R-134a/R-1234yf (44/56)

LowGWPAREPR134aW/CScrewChillerTestSummary – FinalReportcreated:19November2012

lastedited:19November2012page2of16

TraneMP_Report#1_external_121119.docx Ken Schultz•ThermalSystemsGroup

INTRODUCTION

Thisreportdocumentstestsrunonanominal230‐tonwater‐cooledscrewcompressor‐basedwaterchillerinTrane’sLaCrosse,Wisconsin,laboratory.Therefrigerantstestedarelistedbelow:

name supplier order begin testing end

testing number of runs

R134a (#1) (self) 1 16‐May‐2012 23‐May‐2012 38

XP10 DuPont 2 29‐May‐2012 11‐Jun‐2012 24

N‐13a Honeywell 3 13‐Jun‐2012 20‐Jun‐2012 34

N‐13b Honeywell 4 25‐Jun‐2012 29‐Jun‐2012 33

R1234ze(E) Honeywell 5 06‐Jul‐2012 13‐Jul‐2012 40

ARM‐42a Arkema 6 20‐Aug‐2012 11‐Oct‐2012 67

R134a (#2) (self) 7 15‐Oct‐2012 16‐Oct‐2012 13

R1234yf Honeywell 8 Dec‐2012 ?

D4Y Daikin Daikincouldnotsupplyenoughrefrigerantforthechiller.TestswithR134awererepeatedattheendasacheck;performanceverycloselyduplicatedtheoriginalbaselinedataset.TestswithR1234yfwillbeconductedif/whenHoneywellcansupplythevolumeofrefrigerantneeded.DaikinwasunabletoprovidesufficientvolumeofD4Yforthetestchillerusedhere.

TESTSETUP

Thechillertestedhereisanominal230‐ton“RTWD”dual‐circuitwater‐cooledscrewcompressor‐basedwaterchiller.Thespecificunittestedisapre‐productionprototypebuiltfordesignverificationtestinginthelaboratory.Thechillerunderwentseveralmodificationsduringprevioustesting,includingachangetohighliftcompressors,cupronickelcondensertubes,andalternativecopperevaporatortubes.PhotosofthechillerareshowninFigure1.Thechillerconsistsoftwoindependentrefrigerantcircuits.Tominimizetheamountofrefrigerantneeded,testsherewererunwithonlyonecircuit.Thecircuitadjacenttothechilledandcoolingwaterconnectionswasused.Thesecondcircuitwaschargedwithnitrogenat5psigtominimizeheattransferbetweenthewaterpasses.Theevaporatorusesfallingfilmtechnologyinconjunctionwithafloodedpool.Thecondenserincorporatesaliquidrefrigerantsubcooler.Thecompressorrunsatfixedspeed(noAFD).Primaryinstrumentationincluded:

Chilledwaterloopo volumeflowrate(magneticflowmeter)o inletandoutlettemperatures(dualRTD’sateachlocation)o absolutepressurescollocatedwithtemperaturemeasurementso water‐sidepressuredrop

Coolingwaterloopo volumeflowrate(magneticflowmeter)o inletandoutlettemperature(dualRTD’sateachlocation)o absolutepressurescollocatedwithtemperaturemeasurementso water‐sidepressuredrop

CompressorpowerinputThecollocatedtemperatureandpressuremeasurementsareusedtocomputetheinletandoutletenthalpiesofthewater.Heattransferrateiscalculatedastheproductofthewatermassflowrateandthedifferencebetweentheinletandoutletenthalpies.Thecompressor‐basedEERiscalculatedastheratioofthechilledwaterheattransferratetothecompressorpowerinput.




Secondaryinstrumentationincludesvarioustemperatureandpressuremeasurementsalongtherefrigerantflowpath.Keymeasurementsincludethetemperatureandpressureatthecompressorsuctionanddischargealongwiththecondenserliquidleavingtemperatureandpressure.AlistofinstrumentationisincludedasAppendixA.

METHODOFTEST

ThemethodoftestisconsistentwithAppendixCofAHRIStandard550/590‐2011withoperatingconditionsgenerallyheldwithintightertolerances.Performanceisreportedhereasmeasured;noadjustmentsaremadeforfoulingallowance.Thecoolingcapacitiesreportedarecalculatedfromthemeasuredchilledwaterflowrateandthedifferencebetweentheenteringandleavingchilledwaterenthalpies.Theenthalpiesarecomputedfromthemeasuredwatertemperaturesandpressures(collocated).Therefore,thecapacitiesreportedherecorrespondtothe“grossrefrigeratingcapacity”definedinAHRIStandard550/590‐2011.ThermodynamicpropertiesofwaterarecomputedusingTrane’sinternalcode,whichisconsistentwiththe550/590equationstowellwithinexperimentalaccuracies.Thetestmatrixconsistedofthefollowingsteps:

1. Refrigerantchargesweepatbaselineoperating(boundary)conditionsof:–leavingchilledwatertemperature=44°F0.1°Fd(2s)–chilledwaterflowrate=550gpm2gpm–enteringcoolingwatertemperature=85°F0.1°Fd–coolingwaterflowrate=700gpm2gpmThechargeforfurthertestingwasselectedatmaximumEER(5lbmresolution)withconsiderationgiventotherefrigerantlevelinthecondenser/subcooler.

2. Loadlineat100%,90%,80%,70%,60%,minwith“baseline”flowrates:–leavingchilledwatertemperature=44°F0.1°Fd(2s)–chilledwaterflowrate=550gpm2gpm–enteringcoolingwatertemperature=85°F0.1°Fd–coolingwaterflowrate=700gpm2gpm

3. Loadlineat100%,90%,80%,70%,60%,minwith“standard”flowrates:–leavingchilledwatertemperature=44°F0.1°Fd(2s)–chilledwaterflowrate=2.4gpm/ton×tons@100%×2–enteringcoolingwatertemperature=85°F0.1°Fd–coolingwaterflowrate=3.0gpm/ton×tons@100%×2

4. Variationincoolingwaterenteringtemperaturewith–leavingchilledwatertemperature=44°F0.1°Fd(2s)–chilledwaterflowrate=510gpm2gpm–enteringcoolingwatertemperature=85°F0.1°Fd–coolingwaterflowrate=635gpm2gpm

Notethatthewaterflowrateswerebasedonfullchillercapacity(ie,asifbothcircuitswereactive).Runningthewaterflowratesbasedonthesinglecircuitcapacitywouldresultinverylowwatervelocitiesinthetubesandpoorwater‐sideheattransfercoefficients.Inhindsight,itmighthavebeenmoreappropriatetoelevatetheenteringcoolingwatertemperatureby5°FdorsotobemoreconsistentwithAHRI550‐590standardratingconditions.Intheend,consistentconditionswereusedthatprovideafaircomparisonamongthedifferentalternativerefrigerantstested.Figure2showstheenergybalanceclosureerrorsforallofthetestpointsrun.Energybalanceerrorsweregenerallylessthan1%.Thisdemonstratesthestabilityandaccuracyoftheprimarytestmeasurements.




alternativerefrigerantsarealllowerthanforR134a,exceptforthethirdARM‐42adataset.2TheXP10HTC’sarejustslightlylowerthanforR134a.Theshell‐sideHTC’sforR1234ze(E)wereroughly30%lowerthanforR134a.Thisappearscontrarytorecentlypublishedsingle‐tubepoolboilingdata.3TheUoEforR1234ze(E)isalsonegativelyimpactedbythereducedtubein‐sideHTCduetothereductioninchilledwaterflowratewhenoperatingwithreducedcapacityatthestandardflowrates.N‐13aandN‐13bhadverypoorevaporatorperformance.Thiscouldpossiblybeattributabletothe~1°Fdglideassociatedwiththesetwoblends.Visualobservationsindicatedthatthebundlewettingappearedtobesimilarforallrefrigerants;therewerenoobviousindicationsofunusualdry‐outorcarryoverforanyoftherefrigerants.Thereweresomevariationsinoilfoamingbehaviorinthepoolsection(eg,thebubblesizeswerelargerforR1234ze(E),indicativeofthehighervaporspecificvolume),buttheywereminoranddidnotappeartoimpactevaporatorperformance.ThebundleaverageheattransfercoefficientsforthecondenserrelativetoR134aareshowninFigure10.Relativelymildtomoderatereductionsincondensershell‐sideheatcoefficientswereobservedforR1234ze(E),XP10,N‐13a,andN13b.Curiously,theN‐13blends(with~1°Fdglide)appearedtohavesufferedagreaterdegradationinevaporatorperformancethancondenserperformance.AfterseeingverypoorcondenserheattransferperformanceduringtheinitialtestsetwithARM‐42a(#1),arefrigerantsamplewascollectedfromthechillercondenservaporspace,appearingtoindicateanon‐condensablesconcentrationof1.5%vol.4Therefrigerantchargewasreclaimedbackintotheoriginaltwocylindersandthecylindervaporspaceventeduntilthenon‐condensablesconcentrationswere0.96%voland0.78%vol.5ThechillerwasthenrechargedwithARM‐42aandthetestsetrepeated(#2).Condenserperformanceimprovedmarginally,butwasstillquitepoor.Thecondenservaporspacewasagainsampled,thistimewithanon‐condensablesconcentrationof0.9%vol.Therefrigerantwasagainreclaimedintothecylinders.Samplestakenfromcylindersshowedanon‐condensablesconcentrationof~1.5%vol.Thecylinderswereagainventeduntilthenon‐condensablesconcentrationswere0.5%voland0.7%vol.ThechillerwasthenrechargedwithARM‐42aandthetestsetrepeatedathirdtime(#3).Condenserperformanceagaindidnotchange.Arefrigerantsampleextractedfromthecondenservaporspaceshowedanon‐condensablesconcentrationofonly0.3%vol.Whenreclaimedbackintothecylinders,thenon‐condensablesconcentrationwasmeasuredtobeonly0.6%vol.Asnotedabove,curiouslyduringthethirdARM‐42atestset,theevaporatorheattransferperformanceincreasedsignificantly.Thereasonforthisisunknown.ArepeatofthebaselinewithR134a(Oct)followingtheARM‐42atestsproducedresultsveryconsistentwiththeinitialbaselinetestset(May).ThecomparisonsshownherearebasedontheoverallbetterperformanceofthethirdARM‐42adataset.Thesourceofthenon‐condensablesfoundintheARM‐42atestsisunknown.Weareconfidentinourlaboratoryprocedureswithrespecttochillerevacuationandcharging.AdditionalprecautionsweretakenduringpreparationandchargingforthethirdtestofARM‐42atoensurenointroductionofairduringtheprocess.Theisentropicefficiencyofthecompressorcanbedeterminedfromthemeasuredtemperaturesandpressuresatthecompressorsuctionanddischargealongwiththerefrigerantthermodynamicpropertiesdescriptionprovidedbytherefrigerantsuppliers.Theresultsobtainedhereforthefull‐loadcapacitypointsrunwithstandardwaterflowratesareshowninFigure11.Thecompressorperformedsimilarlyforallrefrigerants,mostrunningslightlybelowR134a(∆η~0..0.02).TheN‐13bpointinFigure11issomewhatofanoutlier;thepart‐loadpointsallfellatorbelowtherespectiveR134apoints.2Morebelow.ThefirsttwoARM‐42adatasetsproducedevaporatorHTC’sthatfellbetweenXP10andR1234ze.3EvanRooyenandJRThome,“POOLBOILINGONENHANCEDBOILINGTUBESWITHR‐134a,R‐236faANDR‐1234ze”,ECI8thInternationalConferenceonBoilingandCondensationHeatTransfer,EcolePolytechniqueFédéraledeLausanne,3‐7June2012,Lausanne,Switzerland.4Thenon‐condensablegaseselutedfromtheGCcolumnatthetimeindicativeofbeingair.5Theconcentrationsarebelowthe1.5%volupperlimittypicalofmostrefrigerantslistedinAHRIStandard700.




considerationwillneedtobegiventodesignofthecondensercoilforair‐cooledchillerproductsusingR1234ze(E).AllofthealternatefluidssufferedtosomeextentwithregardtoheattransferperformancerelativetoR134a.ThepoorperformanceofARM‐42ainthecondenserremainspuzzlingatthispoint.Furtherstudyofbothevaporation/boilingandcondensingbehavioroftheserefrigerantsonenhancedtubesiswarranted.Theconsistencybetweencalculatedsaturationandmeasuredtemperatures,alongwithgeneralagreementamongthecompressoradiabaticefficienciesandsuctionvolumeflowrates,indicatesthattherefrigerantpropertiesdescriptionsprovidedarereasonablyaccurate.

NOMENCLATURE

BL “baseline”operatingconditionsasdescribedinMethodofTestsection

CAP CapacityChrg refrigerantchargeCOP CoefficientofPerformance;seeEEREB EnergybalanceclosureerrorEER EnergyEfficiencyRatio=cooling

capacitydividedbyelectricalpowerinputtothecompressor[Btu/W·hr]

°Fd temperaturedifferenceinFahrenheitFC,FC’s “foulingchecks”;essentiallyrepeat

pointstakenataspecificoperatingcondition

HTC heattransfercoefficienthoC’, , shell‐sideheattransfercoefficientin

thecondenserbundlehoE, , shell‐sideheattransfercoefficientin

theevaporatorbundlePmsrd measuredpressureq"C averageheatfluxinthecondenserq"E averageheatfluxintheevaporatorQChW, heattransferratecomputedfrom

measurementsofthechilledwaterQClW, heattransferratecomputedfrom

measurementsofthecoolingwater

Std “standard”operatingconditionsasdescribedinMethodofTestsection(inparticular,standardevaporatorchilledwaterflowis2.4gpm/maxtonandstandardcondensercoolingwaterflowis3.0gpm/maxton)

∆TappC,dTappCapproachtemperatureinthecondenser(condensersaturationleavingcoolingwatertemperature)

∆TappE,dTappEapproachtemperatureintheevaporator(leavingchilledwaterevaporatorsaturationtemperature)

∆Tsc refrigerantsubcoolingleavingthecondenser/subcooler(refrigerantsaturationtemperatureactualtemperature)

Tmsrd measuredtemperatureTsat saturationtemperatureUoC, , overallheattransfercoefficientinthe

condenserbundleUoE, , overallheattransfercoefficientinthe

evaporatorbundleWcmpr, compressorpowerconsumptionx refrigerantqualityinthetwo‐phase

regionηCmpr adiabaticefficiencyofthecompressor

T&Pmeasurementstationsforcoolingandchilledwaterloops.

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Appendix A – Instrumentation List

ID # ** Description Units Type Measurement Accuracy1 EVAP WATER FLOW GPM SI: m³/h Rosemount Magnetic ± 0.5% of Rdg2 EVAP Unit water delta Press psid SI: kPa∙diff Rosemount 1151 ± 0.054 PSID3 Evap unit water press ‐ ent psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA4 Evap unit water press ‐ lvg psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA5 COND WATER FLOW GPM SI: m³/h Rosemount Magnetic ± 0.5% of Rdg6 Cond Unit Water Delta Press psid SI: kPa∙diff Rosemount 1151 ± 0.054 PSID7 Cond Unit Water Press ‐ ent psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA8 Cond Unit Water Press ‐ lvg psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA

100 Evap Shell Press (1) ‐ Ckt #1 psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA105 Evap Shell Press (2) ‐ Ckt #1 psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA110 Comp Suct Refrig Press ‐ Ckt #1 psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA115 Comp Disch Refrig Press ‐ Ckt #1 psia SI: kPa∙abs Sensotec DS – 500 psia ± 0.25 PSIA125 Cond Top Shell Press Loc 1 ‐ Ckt # 1 psia SI: kPa∙abs Sensotec DS – 500 psia ± 0.25 PSIA126 Cond Top Shell Press Loc 2 ‐ Ckt # 1 psia SI: kPa∙abs Sensotec DS – 500 psia ± 0.25 PSIA130 Lvg Subcooler Refrig Press ‐ Ckt 1 psia SI: kPa∙abs Sensotec DS – 500 psia ± 0.25 PSIA137 Ent Evap Refrig Press Ckt #1 psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.25 PSIA215 Comp Disch Temp ‐ Ckt #1 °F SI: °C Type T TC ± 1.0 F240 Ent Evap Refrig Temp Ckt #1 °F SI: °C Type T TC ± 1.0 F250 Comp Suct Refrig Temp Ckt #1 °F SI: °C Type T TC ± 1.0 F251 Line Lvg Oil Separator T Ckt #1 °F SI: °C Type T TC ± 1.0 F330 Evap RI probe Temp ‐ Loc 1 ‐ Ckt 1 °F SI: °C Type T TC ± 1.0 F331 Evap RI probe Temp ‐ Loc 2 ‐ Ckt 1 °F SI: °C Type T TC ± 1.0 F332 Evap RI probe Temp ‐ Loc 3 ‐ Ckt 1 °F SI: °C Type T TC ± 1.0 F400 ENT EVAP WATER TEMP LOC 1 °F SI: °C 100 Ω RTD ± 0.1 F401 ENT EVAP WATER TEMP LOC 2 °F SI: °C 100 Ω RTD ± 0.1 F402 LVG EVAP WATER TEMP LOC 1 °F SI: °C 100 Ω RTD ± 0.1 F403 LVG EVAP WATER TEMP LOC 2 °F SI: °C 100 Ω RTD ± 0.1 F405 ENT COND WATER TEMP LOC 1 °F SI: °C 100 Ω RTD ± 0.1 F406 ENT COND WATER TEMP LOC 2 °F SI: °C 100 Ω RTD ± 0.1 F407 LVG COND WATER TEMP LOC 1 °F SI: °C 100 Ω RTD ± 0.1 F408 LVG COND WATER TEMP LOC 2 °F SI: °C 100 Ω RTD ± 0.1 F410 Evap Sat RTD ‐ Ckt #1 °F SI: °C 100 Ω RTD ± 0.1 F417 Lvg subcooler refrigerant RTD ‐ Ckt #1 °F SI: °C 100 Ω RTD ± 0.1 F420 Compressor VOLTAGE AB ‐ Ckt # 1 V SI: V421 Compressor VOLTAGE AC ‐ Ckt # 1 V SI: V422 Compressor VOLTAGE CB ‐ Ckt # 1 V SI: V423 Compressor CURRENT A ‐ Ckt # 1 A SI: A ~0.5% of Rdg w/ CTs424 Compressor CURRENT B ‐ Ckt # 1 A SI: A ~0.5% of Rdg w/ CTs425 Compressor CURRENT C ‐ Ckt # 1 A SI: A ~0.5% of Rdg w/ CTs426 Compressor Power ‐ Ckt # 1 W SI: W ~0.5% of Rdg w/ CTs427 Compressor Power ‐ Frequency ‐ Ckt # 1 Hz SI: Hz428 Compressor Power ‐ Power Factor ‐ Ckt # 1 None SI: NONE480 Evap RI probe ‐ loc 1 ‐ ckt 1 % SI: %481 Evap RI probe ‐ loc 2 ‐ ckt 1 % SI: %482 Evap RI probe ‐ loc 3 ‐ ckt 1 % SI: %496 Leaving Oil Separator RI Probe ‐ ckt 1 % SI: %500 BAROMETRIC PRESS FROM METROLOGY psia SI: kPa∙abs ± 0.0157 PSIA600 Chiller : Liquid Level Setpoint in SI: mm N/A601 Circuit 1 : Refrigerant Liquid Level in SI: mm N/A602 Circuit 2 : Refrigerant Liquid Level in SI: mm N/A




AppendixB

DataPointsCollectedatFull‐LoadCapacityWhenRunningattheStandardOperatingConditions

(InsertthepagesfromTraneMP_Report#1_DataForms.pdffollowingthispageinthePDF.)

Appendix BData Points Collected at Standard Operating Conditions

Low GWP AREP SYSTEM DROP‐IN TEST DATA FORM page 1

Manufacturer: Trane

Basic Information

Alternative Refrigerant XP10 DuPontAlternative Lubricant Type and ISO Viscosity POE – 68Baseline Refrigerant R134aBaseline Lubricant Type and ISO Viscosity POE – 68Make and Model of System RTWD water‐cooled chiller (running first of two refrigerant circuitsNominal Capacity and Type of System 230 nominal tons (preproduction prototype for lab verification)

Comparison Data Base Alt. SI Units Base Alt. IP Units RatioMode (heating/cooling) coolingCompressor Type screw compressor (high lift version)Compressor Displacement m³/hr cfmNominal Motor Size kW hpMotor Speed (60 Hz) HzExpansion Device Type electronic expansion valveLubricant Charge L galRefrigerant Charge 81.6 81.6 kg 180 180 lbm 1.000Composition (at Cmpr Suct)

6.7 6.7 °C 43.98 44.00 °F 0.021928 1927 L/min 509.3 509.2 gpm 1.000

Flow rate (tons × 2) 5.2 5.2 L/min∙kW 2.41 2.41 gpm/ton 1.00229.5 29.5 °C 85.0 85.1 °F 0.02409 2409 L/min 636 636 gpm 1.000

Flow rate (tons × 2) 6.5 6.5 L/min∙kW 3.01 3.01 gpm/ton 1.002Capacity 371.9 371.2 kW 105.7 105.5 tons 0.998Power to Compressor 86.0 89.6 kW 86.0 89.6 kW 1.043COP or EER (compressor only) 4.33 4.14 [] 14.76 14.13 Btu/W∙hr 0.957Refrigerant Mass Flow Rate 8,596 9,961 kg/hr 18,950 21,960 lbm/hr 1.159Refrig Flow @ Cmpr Suction 518.2 514.3 m³/hr 305.0 302.7 cfm 0.992

Other System ChangesThe unit tested has non‐standard evaporator tubes (alternate high performance design).The unit tested has non‐standard condenser tubes (90/10 cupronickel).Only one of two refrigerant circuits was run due to limited availability of some refrigerants.

System Data Base Alt. RatioDegradation CoefficientSeasonal Energy Efficiency Ration – SEERHeating Seasonal Performance Factor – HSPF

12 3.1

Chilled Water

Leaving TempFlow rate

Cooling Water

Entering TempFlow rate

08‐Nov‐2012



Type of System: RTWD wc Water Chiller Alternate Refrigerant: XP10

Water Side Data Base Alt. SI Units Base Alt. IP Units Ratio | Diff

Evaporator (shell & tube)fluidflow rate 1928.0 1927.4 L/hr 509 509 gpm 1.000T entering 9.4 9.4 °C 48.9 48.9 °F 0.0°FT leaving 6.7 6.7 °C 44.0 44.0 °F 0.0°Fpressure drop 121 114 kPa 17.5 16.5 psid 0.945

Condenser (shell & tube)fluidflow rate 2408.9 2408.5 L/hr 636 636 gpm 1.000T entering 29.5 29.5 °C 85.0 85.1 °F 0.0°FT leaving 32.2 32.3 °C 90.0 90.1 °F 0.1°Fpressure drop 140 136 kPa 20.3 19.7 psid 0.969

Refrigerant Side T (°C) P (kPa) T (°C) P (kPa) T (°F) P (psia) T (°F) P (psia)

Compressor (screw)suction 3.9 338 3.7 367 39.0 49.0 38.7 53.2discharge 51.2 943 47.5 1007 124.2 136.8 117.4 146.0dchrg SH | Pratio 14.0 9.5 25.2 2.79 17.15 2.75

Condenser (shell & tube w/integral subcooler)inlet/shell 51.2 943 47.5 1,007 124.2 136.8 117.4 146.0shell dewpoint 36.4 37.0 97.6 98.6shell bubblept 36.4 37.0 97.6 98.6subcooler outlet 32.5 911 32.5 964 90.5 132.1 90.5 139.8subcooling (local) 3.5 3.8 6.2 6.8

Expansion Device (EXV)inlet 32.5 911 32.5 964 90.5 132.1 90.5 139.8

Evaporator (shell & tube)inlet/shell 4.3 341 4.2 370 39.7 49.5 39.5 53.7outlet/shell 4.3 341 4.2 370 39.7 49.5 39.5 53.7

Refrigerant Side Base Alt. SI Units Base Alt. IP Units Ratiosuction line pressure drop 3.2 3.7 kPa 0.46 0.53 psid 1.16discharge line pressure drop 20 25 kPa 2.90 3.59 psid 1.24

08‐Nov‐2012

water

water

Base Alt. Base Alt.



Manufacturer: Trane

Basic Information

Alternative Refrigerant N‐13a HoneywellAlternative Lubricant Type and ISO Viscosity POE – 68Baseline Refrigerant R134aBaseline Lubricant Type and ISO Viscosity POE – 68Make and Model of System RTWD water‐cooled chiller (running first of two refrigerant circuitsNominal Capacity and Type of System 230 nominal tons (preproduction prototype for lab verification)


6.7 6.6 °C 43.98 43.93 °F ‐0.061928 1708 L/min 509.3 451.3 gpm 0.886





12 3.1

Chilled Water


Cooling Water


08‐Nov‐2012



Type of System: RTWD wc Water Chiller Alternate Refrigerant: N‐13a


Evaporator (shell & tube)fluidflow rate 1928.0 1708.3 L/hr 509 451 gpm 0.886T entering 9.4 9.4 °C 48.9 48.8 °F ‐0.1°FT leaving 6.7 6.6 °C 44.0 43.9 °F ‐0.1°Fpressure drop 121 96 kPa 17.5 14.0 psid 0.799




Condenser (shell & tube w/integral subcooler)inlet/shell 51.2 943 48.2 893 124.2 136.8 118.7 129.5shell dewpoint 36.4 36.7 97.6 98.1shell bubblept 36.4 36.1 97.6 97.0subcooler outlet 32.5 911 32.6 861 90.5 132.1 90.8 124.9subcooling (local) 3.5 2.9 6.2 5.3




08‐Nov‐2012

water

water

Base Alt. Base Alt.



Manufacturer: Trane

Basic Information

Alternative Refrigerant N‐13b HoneywellAlternative Lubricant Type and ISO Viscosity POE – 68Baseline Refrigerant R134aBaseline Lubricant Type and ISO Viscosity POE – 68Make and Model of System RTWD water‐cooled chiller (running first of two refrigerant circuitsNominal Capacity and Type of System 230 nominal tons (preproduction prototype for lab verification)


6.7 6.7 °C 43.98 43.98 °F 0.001928 1636 L/min 509.3 432.3 gpm 0.849





12 3.1

Chilled Water


Cooling Water


08‐Nov‐2012



Type of System: RTWD wc Water Chiller Alternate Refrigerant: N‐13b










08‐Nov‐2012

water

water

Base Alt. Base Alt.



Manufacturer: Trane

Basic Information

Alternative Refrigerant R1234ze HoneywellAlternative Lubricant Type and ISO Viscosity POE – 68Baseline Refrigerant R134aBaseline Lubricant Type and ISO Viscosity POE – 68Make and Model of System RTWD water‐cooled chiller (running first of two refrigerant circuitsNominal Capacity and Type of System 230 nominal tons (preproduction prototype for lab verification)


6.7 6.6 °C 43.98 43.96 °F ‐0.021928 1417 L/min 509.3 374.2 gpm 0.735





12 3.1

Chilled Water


Cooling Water


08‐Nov‐2012



Type of System: RTWD wc Water Chiller Alternate Refrigerant: R1234ze










08‐Nov‐2012

water

water

Base Alt. Base Alt.



Manufacturer: Trane

Basic Information

Alternative Refrigerant ARM‐42a ArkemaAlternative Lubricant Type and ISO Viscosity POE – 68Baseline Refrigerant R134aBaseline Lubricant Type and ISO Viscosity POE – 68Make and Model of System RTWD water‐cooled chiller (running first of two refrigerant circuitsNominal Capacity and Type of System 230 nominal tons (preproduction prototype for lab verification)


6.7 6.7 °C 43.98 43.99 °F 0.011928 1856 L/min 509.3 490.4 gpm 0.963





12 3.1

Chilled Water


Cooling Water


08‐Nov‐2012



Type of System: RTWD wc Water Chiller Alternate Refrigerant: ARM‐42a










08‐Nov‐2012

water

water

Base Alt. Base Alt.

test report coversheet-Rpt-007Low-GWP AREP-Rpt-007test report coversheet-Rpt-007Low-GWP AREP-Rpt-007_Trane

TEST REPORT #7 System Drop-In Tests of R134a Alternative ......Low GWP AREP R134a W/C Screw Chiller...

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