压缩式制冷系统

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1、TheDesignofRefrigerationSysteminAir-conditionerMembers:李雨柏鲁力吕品吴信信项靖海洪英挺DivisionofLabourWedividethedesignintosixpartpartoneandfour:鲁力parttwo:吴信信项靖海partthreeandfive:李雨柏partsix:洪英挺report:吕品BackgroundofRefrigerationSystemAnairconditionerisrequiredtocarrychi

2、lledwaterwhichis8°Cdegreestoafamily.Theaveragetemperatureofreturnwateris15°C.Weusethecirculatingwaterasheadwaters.Thewholecoolingcapacityis700KW.Thetemperatureofcoolingwateris35°C.Pleasedesigntherefriferationsystem.Ourrefrigerationsystem排节流装置Equipmentch

3、oosingCondenser：VerticalShell-TubeCondenser,LN-120Evaporator:horizontalshellandtubeevaporatorCompressor:6w-12.5、8s-12.5Driveingmotor:90KW、115KWExpansionvalve:verticalexternalbalanceexpansionvalveaccumulator:ZA-2Ammoniaoilseparator:YF-80BStepofcalculatio

4、nStep1RefrigerationconditionEvaporationtemperaturetE：tE=8-5=3°CCondensingtemperaturetC:Itisfivedegreeshigherthantheaveragetemperatureofcoolingwaterfromentrancetoexit.InAmmoniaVerticalShell-TubeCondenser,thetemperaturebetweenentranceandexitcanbeasmuchasf

5、ivedegrees.tw2=tw1+5=35+5=40°CtC=(twl+tw2)/2+5.5=43°CStep2DriveingmotorandCompressorcoolingcapacityQr=(1.0+0.15)*700=805KWdegreeofsuperheatincompressorisfivedegrees.qv=(hl-h4)/v1=(1460.22-405.12)/0.2718=3881.90KJ/m3tE=3°C,pE=0.500MpatC=43°C,pC=1.757MpaS

6、uctioncoefficient:nv=0.7981,vh=Qr/(nv*qv)=0.260m3/stheoreticalgasof6w-12.5:vh1=0.118m3/stheoreticalgasof8s-12.5:vh2=0.157m3/sVh=vh1+vh2=0.275m3/s>vhSowechoosetwocompressor,oneis6W-12.5,theotheris8s-12.5Thecoolingcapacityof6w-12.5:Qrl=§v*qv*vhl=365.58KWT

7、hecoolingcapacityof8s-12.5:Qr2=§v*qv*vh2=486.41KWThewholecoolingcapacity:QR=Qrl+Qr2=851.99KW>Qrsotheyaresuitable.theoreticalpowerof6w-12.5:Pth1=mR*w=56.49KWIndicatingefficiencyof6w-12.5isni=0.82Mechanicalefficiencyof6w-12.5isnm=0.87IndicatingpowerPi=Pth

8、l/ni=68.89KWshaftpowerPB=Pi/nm=79.18KWpowerofdrivingmotor:PD=1.1PB=87.1KWsothepowerofmotorwhatdrives6W-12.5is90KWtheoreticalpowerof8s-12.5:Pth2=mR*w=75.16KWIndicatingefficiencyof8s-12.5isni1=0.85Mechanicalefficiencyof8s-12.5isnml