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XVI A new sky temperature calculating method used for designing the nocturnal cooling systems3 ) PCM ( 4Under-FloorHeatingSystems:ComputationalpredictionofOptimumConvectionHeatTransfer Coefficient5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 ) ( 20 21 25 3 1 29Experimental Analysis of Aircraft Individual Air Distribution System Design30 31Criteria of Effectiveness Evaluation of centrifugal pumps in district heating systems32 35 ) -3 2O AL( 36 37 (HCCI) 38 XVII ) MCHP ( 39 40 41 42 - 43 44 45Experimental Approach to Enhance Solar Water Heater using Phase Change Materials 46THETRIALSANDTRIBULATIONSOFCREATINGANHFC/HCFCFREEFOODROCESSING PLANT BY INSTALLING A TWO STAGE TRANSCRITICAL CO2 REFRIGERATION PLANT 49THE ENERGY EFFICIENCY IN OFFICE BUILDINGS AND HOSPITALS USINGTOTAL ENERGY NH3AND CO2 SYSTEMS SEPARATELY AND COMBINEDFOR HEATING AND COOLING 50 51Investigationofleakedairintocycleanditspurgingeffectsonaircoolingchillercycleofcryogenic nitrogen generation unit 52 55 56 57 58 61 62 63 64 65 66 69 70 71 72 XVIII GSHP 73 74 75 76 77 78 79 80 81 82 83 ) capillary heatexchanger ( 84 - 85 89 90 91 92

A New Sky Temperature Calculating Method Used For Designing the Nocturnal Cooling Systems Maryam Karami1, Moien Farmahini-Farahani2, Shahram Delfani3 1Department of Mechanical Engineering, Faculty of Engineering, University of Tehran, m.karami53@gmail.com 2School of Aerospace and Mechanical Engineering, University of Oklahoma, USA. 3Department of Installation, Building and Housing Research Center (BHRC), Tehran, Iran Abstract Theskytemperatureaffectsperformanceofsolarheatingandnocturnalcoolingsystems.Nocturnal coolingsystemsarecategorizedinPassivecoolingsystem.Passivecoolingresources,thesky, atmosphere, and earth, are the natural heat sinks of the planet earth. The dissipation of heat carried out bylong-waveradiationfromabuilding totheskythatiscalledradiativecooling.Inthissystem,the waterinastoragetankiscooledbymeansofcirculatingthewaterthroughaflat-plateradiator throughoutanight(nocturnalradiativecooling).Duringthenextday,thecoldwaterinthestorage tankisusedforcoolingthehotoutdoorair.Thissystemcanbealsousedasahybridsystemwith direct evaporative cooling. Sinceskytemperatureisafunctionoftheambienttemperature,itisobvioususingclimaticdesign conditions result in more accurate sky temperature calculations, leading to estimate the potential of the nocturnal cooling more precisely. In this study, the Bin method has been used to analysis climatic data andreachdesignvaluesthatoccurmorefrequently.Thismethodisthemostimportantsteady-state modelusedtocalculatethedesigncondition.Inordertoanalysisbythismethod,binweatherdata should be evaluated with long-term measured data. Hourly DBT and WBT from the Islamic republic ofIranMeteorologicalOrganization(IRIMO)wereusedforthecalculationofdesignconditions. Bin data for dry-bulb and wet-bulb temperatures were calculated in eight daily three-hour shifts (13, 46,79,1012,1315,1517,18-21,22-24h)fortheimportantcitiesofIranshowedinFigure1. The most cities are capital of 30 states of Iran. Usingbinmethodcausestheoutdoordesignconditionandskytemperaturesareevaluatedmore accurately. Then the difference of the ambient and sky temperature, sky temperature depression can be determinedprecisely.Theseareusedinsolarheatingandnocturnalcoolinginurbanbuildings.In this research, at first, the new climatic design conditions were calculated for important cities of Iran; thenthesenewdry-bulb(DBT)andwet-bulbtemperatures(WBT)wereusedtocalculatethesky temperature. Then, monthly clear sky temperature contours of a multi-climate country, Iran, have been depicted. As the results, Iran cities based on the local clear sky temperature variation are categorized in four regions. 1135 ) PCM ( 1 21 armanmaroufi@yahoo.com2 aghanajafi@kntu.ac.ir . . ) PCMs ( . . . PCM . ) LBM ( . . . D2Q9 BGK . . . .1159 Under-Floor Heating Systems: Computational prediction of Optimum Convection Heat Transfer Coefficient a Amin Engarnevis1, Hadi Jafari2, Majid Amidpour3 1,2Faculty of Mechanical Engineering, KNT University of Technology; amin.engarnevis@gmail.com, Hadijafari7@gmail.com 3Energy systems Engineering Department, Faculty of Mechanical Engineering, KNT University of Technology; amidpour@kntu.ac.ir Abstract Inthisstudy,inafloorheatedroom,optimumnaturalconvectionheattransferovertheflooris analyzednumericallyforconstantspecificconditionssuchas;Temperatureofsupplywater,design temperature,outsidetemperature,thicknessofconcreteonwatertubes,distanceamongwatertubes and,etc.Inthiscondition,anoptimumheattransfercoefficientofairalwaysexistsforwhich maximum heat transfer from the floor takes place. In this paper, above parameters are introduced and the effect of thickness of concrete on heat transfer is investigated. Subsequently, the effect of different amountsofconvectionheattransfercoefficientofmovingambientairontheobtainedheattransfer from the surface of the concrete is studied. Results showed that thickness of concrete has a great effect on fluxes of energy obtained from the coverage, ex. marble. And by using less thickness of concrete, morefluxesofenergyisobtained.Also,consequencesarenotedthatbydifferentamountsof mentionedparameter,variousamountsofthermalenergyfromthesurfaceoftheconcreteare available. This optimum convection heat transfer coefficient can be obtained through an electrical fan to get a more economical thermal power from the surface. Keywords: Under-Floor Heating, Wirsbo Model, Optimum Convection Heat Transfer Coefficient

Industrial/Professional Applications Results of the paper can be applied for designing optimum under-floor heating systems. Results are shown if concrete be used as coverage on water tube, with increasing thickness and distance of tubes, heat flux in floor increases and reduces respectively. This note can be applied in installation and design of these systems and using various overages can be studied. Utilization Electric fan can be useful to reach optimum heat transfer coefficient of room air. Using Wirsbo Model because considering symmetric line as adiabatic boundary conditions makes it easier analyzing under-floor heating systems.1160 1 2 3 41 msalehi_88@yahoo.com2 nazanin_n_a@yahoo.com3 jamal_kh_k@yahoo.com 4 jafar_mami@yahoo.com

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- 3 3 3 1126 Experimental Analysis of Aircraft Individual Air Distribution System Design a Mohammad Hadi Esteki1, SayedMohammad Reza Afghari2, Sattar Shahbaz3

1Air Condition System Expert, Aeronautical Design Center of Iran Aircraft Manufacturing Industries Co.; esteki2005@gmail.com2Air Distribution System Expert, Aeronautical Design Center of Iran Aircraft Manufacturing Industries Co.; mr.afghari2010@gmail.com3 Life Support Systems Dep. Manager, Aeronautical Design Center of Iran Aircraft Manufacturing Industries Co.; sattarshahbaz@yahoo.com Abstract Anenvironmentalcontrolsystem(ECS)isusedtoprotectpassengersandcrewmembersinanaircraftfromdifferent pressure, moisture and temperature of ambient environment. The air distribution system is an important component of the environmental control system since it is used to distribute conditioned air properly to the cabin, providing a healthy and comfortablecabinenvironment.Soitisverychallengingtodesignordevelopacomfortableandhealthycabin environment for aircrafts with special mission. Inordertoaddairgaspersystemasanindividualairdistributionsystemtoanairdistributionsystemofanaircraftwith special mission, simple calculations and experimental validation will be help to achieve design criteria in the best way. The passenger air gasper system is installed in addition to cabin main air supply. The gasper supplies the same conditioned air from the air conditioning pack. The air gaspers are supplied by existing cabin main duct having series of outlet holes/perforations for cabin cooling. The ducting system pressure loss analysis contains a performance calculation based on geometric construction of the upper duct and gasper configuration. The ducting system is assumed has two types of outlets, gasper outlets and upper duct slot outlets. Results show that the minimum velocity of the air at duct perforation holes of 1.87 m/s decreases to 0.98 m/s in the outlet (slot) and the maximum velocity of the air at perforation holes of 12.68 m/s decreases to 3.8 m/s. With all in open position the air flow extracted by gaspers from the duct is 2.29% (4.67 cfm from total ECS supply of 202.95 cfm). Throw distance for duct is calculated about 17 inches. In according to the ECS supply, the air outlet velocity of perforations was measured by velocity gage equipment. The average of each section has been compared with theoretical results. The most different is about 28% that has happened at third section of perforation holes because of flow turbulence intensity and reality condition of air flow throw the duct.Finallydesignresultsshowgoodagreementbetweenairflowthrowgaspersandgaspertopassengerdistancethat makescomfortableairfeelingconditions.Alsotheexperimentalanalysisonthemockupvalidatesresultsofoutlet velocity of gaspers and perforations calculations. Therefore adding of gasper system to available distribution system was designed in according to least modifications, suitable location and good air flow throw gaspers. It was found the upperductairdistributionamonggaspersisrelativelyuniform.Inaddition,theagreementbetweentheairvelocity calculations results and the experimental data is reasonably good. Keywords: Air distribution system, Aircraft, Gasper, Environmental control system, Pressure Loss. Industrial/Professional Applications Results of the article can be applied for aircraft air distribution systems design. Simple calculations and experimental validation will be help to achieve design criteria in the best way. Validating by air distribution mockup in operational condition decrease design risk instead of simulating by some assumptions. 3140 1 2 31 s.shahbazi@modares.ac.ir2 m.amjadi@modares.ac.ir3 gheidari@modares.ac.ir

. . CO NOx . 841 621 202 . . . 5 . ) 10 ( . - ppm 70 101 46 4 .

: - . . CO . ppm 100 . 841 577 . ppm 100 50 . . . 2 . 50 - 60 . .1 PIARC (Permanent International Association of Road Congresses) 2 critical ventilation velocity 3144 Criteria of Effectiveness Evaluation of Centrifugal Pumps in District Heating Systems Egils Dzelzitis1, Deniss Pilscikovs2 1Riga Technical University/Institute of Heat, Gas and Water Technology; egils@lafipa.lv 2Riga Technical University/Institute of Heat, Gas and Water Technology; denpil@inbox.lv Abstract Thegoalofthisresearchisthederivationofcriteriaofeffectivenessevaluationofvariablespeed centrifugal pumps in district heating systems. Forthispurpose,theefficiencylevelofcentrifugalpumpsofvariousdesignshasbeenanalyzedat certain head and flow range. There is also the change of the efficiency level of circulators has been investigated in the article. It has been done at different deviations from the nominal pump head. As a criterion, the effectiveness of the proportional pressure control mode has also been analyzed for centrifugalpumpswithvariablespeedmotors.Ithasbeendoneiftheproportionalpressurecontrol mode is used in comparison with the constant pressure control mode. Forthesereasons,agreatnumberofenergyanalyses havebeenrealizedfordifferentpumpsandthe regression equations with the coefficients of determination have been derived. Astheresult,thethreecriteriaofeffectivenessevaluationofcentrifugalpumpshavebeenderived. Thesecriteriaaredesignofcentrifugalpumps;dutypointlocationcomparativelythenominalpump head;useoftheproportionalpressure.Thetrendofthereductionofenergyconsumptionhasbeen determined. In this connection the regression equations have been derived. The conclusions are as follow: Verticalin-linesingle-stagepumpsarelessefficientincomparisonwithhorizontalend-suction single-stagepumps,whentheflowratevariesfrom20to220m3/hatthedefiniterangeofthehead (from 10 to 72 m). The difference in the efficiency level of the centrifugal pumps is from 3% up to 6% at the definite range of flow and head. The reduction of annual energy consumption can be achieved up to 33%, if the proportional pressure is applied and the deviations from the head value of duty point at zero flow declines up to 60%. The efficiency level drops up to 3% if the deviation of the head value of the best efficiency point is up to 30% from its nominal value. A slight decrease of the efficiency level is observed if the deviation from the nominal head value is up to 30%. If the head deviation is above 30%, then the efficiency level drops rapidly. Keywords: centrifugal pump, control mode, efficiency Industrial/Professional Applications Results of the article can be applied for pump audit in low and medium-scale HVAC systems. ResultsallowincreasingthelevelofefficiencyinHVACsystems,thuscontributingtoenergy saving in the world. Results of the article can be used as a guide for designers with a focus on pumping systems. 5126

1 1 mfallah@azaruniv.edu

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6123 Experimental Approach to Enhance Solar Water Heater Using Phase Change Materials Mohammad Ali Fazilati1, Ali Akbar Alemrajabi2 1PHD student, Mechanical department, Isfahan University of Technology, m_a_fazilati@yahoo.com 2Assistant professor, Mechanical department, Isfahan University of Technology rajabi@cc.iut.ac.ir Abstract Inthisresearch,theeffectsofusingPhaseChangeMaterials(PCM)asstoragemediumonthe performanceofasolarwaterheaterhavebeenexperimentallyinvestigated.Atypeofparaffinwith specialthermodynamicpropertiesisusedasPCMinsphericalcapsulesinconjunctionwithwateras storagematerialinthetankofsolarwaterheater.Thesolarradiationmodeledasweak,meanand strongbycirculatingwaterwiththreetemperaturelevelsof40,60and80oCinjacketoftank.The energy and exergy efficiencies of solar water heater and the time the heater can supply hot water have beencomparedbeforeandafteruseofPCMintank.ItisobservedthatusingPCMinthetankthe energy storage density is increased in the tank up to 39% and the exergy efficiency is enhanced up to 16%.Also,itisobservedthatsolarwaterheaterwithPCM,cansupplyhotwaterwithspecified temperatureat25%largertimecomparedtopurewatertank.Improvementinthermalstratification has been observed by examining temperature histories of different water layers in the tank. Keywords: solar water heater, PCM, Enhancement, energy and exergy efficiency Industrial/Professional Applications Industrialapplicationthatcanbeinferredasaresultofthisworkistechnicaljustificationofusing PCM,especiallyparaffinwax,asastoragematerialinsolarwaterheaters.Keepinginmindthe relativelowcostofparaffinasaPCMagainstothersuchmaterials,thisworkfocusonenhancinga solarwaterheaterfromexergyandenergyaspectsasaresultofemployingparaffininourmodelas proceeded: The time period of supplying water heater is increasedup to 25% The heat storage energy density of tank is increased up to 39% and thus decreases the overall weight of system. Exergyrecoveryofheaterimprovesandconsequentlytheoutletwaterfromheaterequippedwith PCM has a relatively higher temperature, at the same conditions. 8102

The Trials and Tribulations of Creating an HFC/HCFC Free Food Processing Plant by Installing a Two Stage Transcritical CO2 Refrigeration Plant K. Visser KAV Consulting Pty Ltd, P O Box 1146, Kangaroo Flat, Vic, 3555, Australia Tel: (03) 5447 9436 Fax: (03) 5447 9805, kavconsult@bigpond.com Abstract ThetwostagetranscriticalCO2refrigerationplantreplacestwentytwoindependentsystems comprising air cooled HFC and HCFC cooling systems for blast freezing, cold and chill storage, office AC,factorycooling,processwaterchillingandwaterheatingbygasandR134aheatpumps,and electricdefrost,freezerdoorfasciasandunderfloorheating.Ninecompressorsareusedcomprising three high stage compressors and two AC compressors with one common standby plus three boosters including one standby. Operating conditions are +5C SST for office AC, 5C SST for high stage and chilling duties and 40C SST for the cold store and blast freezer. The AC compressors also serve as parallel economizer compressors to reduce the flash gas flow to the rest of the system for chilling and freezingaccountingfor75%ofthesystemshighstagecapacity.ThisproducesahighCOPforthe high stage compressors. TheACandhighstagecompressorsmaydischargeeithertothetwostagegascoolerortwowater heatersinseriestoheatwaterto80C.Insubcriticalmode,thesignificantlyoversizedadiabatically assisted gas cooler will allow condensing at 5 K temperature difference between air entry dry bulb and condensing temperatures. Keywords: Transcritical, CO2 refrigeration, water heating, parallel compression, economizer. 1167 The Energy Efficiency in Office Buildings and Hospitals Using Total Energy NH3 and CO2 Systems Separately and Combined for Heating and Cooling K. Visser KAV Consulting Pty Ltd, P O Box 1146, Kangaroo Flat, Vic, 3555, Australia Tel: (03) 5447 9436 Fax: (03) 5447 9805, kavconsult@bigpond.com Abstract It is becoming increasingly clear that HFC refrigerants are offering a solution to the problem of Ozone Depletion Potential (ODP) associated with CFCs and HCFCs, but have done very little, if anything at all, about the Global Warming Potential (GWP) associated with the use of CFC and HCFC chemical refrigerants.The GWP of the new HFC family of refrigerants is now becoming an increasing concern.The other major issue is the specific energy consumption per squaremetre of occupied building area forbothheatingandcoolingasshowninaUSADepartmentofEnergyreportdealingwithThermal Distribution,AuxiliaryEquipmentandVentilationandtheEnergyConsumptionCharacteristicsof CommercialBuildingHVACsystemsintheUSAcomprising3,345millionm2ofcooledbuilding floor space plus 4,459 million m2 of heated building floor space.AsolutiontoboththeseproblemsispossiblebyusingthenaturalrefrigerantsAmmonia(NH3)and Carbon Dioxide (CO2), both of which were used extensively in building cooling before the advent of chemical refrigerants in the early 1930s.It is shown, that NH3 has already made a significant return inthecoolingofbuildingsbecauseofitsthermodynamicefficiencyandbecauseitsGWP=0.The highpotentialofNH3systemstobeusedforbothcoolingandheatingoflargebuildingsis demonstratedintermsofenergyefficiencyand0GWP.WhenretrofittingNH3chillersandheat pumpsintobuildingsforheatingandcooling,theprimaryenergyconsumption,electricalenergy consumption and attendant emissions per m2 of office building would reduce by 14%, 35% and 30% respectively.In the case of retrofitting CO2chillers with heat recovery, the reductions per m2 would be 18%,52%and33%forelectricalenergyconsumption,primaryenergyconsumptionandemissions respectively. Purpose designed and built CO2 heating and cooling plants for office buildings would yield estimated reductions per m2 of 48% in electrical energy, 59% in primary energy and 57% in emissions, whilst in the case of similar NH3 plants these reductions are estimated at 39%, 54% and 50% respectively. In the case of hospitals the percentage reductions in electrical energy, primary energy and emissions per m2are generally greater when comparing these reductions to those estimated for office buildings for both retrofitting and purpose designed natural refrigerant systems.This is most likely caused by the fact that hospitals operate 24 hours/day, 365 day/year. 1168 1 2 31 ehsan.soltani@gmail.com2 ) ( mostafa.mafi@ikiu.ac.ir3 amidpour@kntu.ac.ir

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Investigation of Leaked Air Into Cycle and Its Purging Effects on Air Cooling Chiller Cycle of Cryogenic Nitrogen Generation Unit Esmaeil Bahmyari1, Hamidreza Miri2, Mostafa Jahankhah3

1Ms in Mechanical Engineering, SPGC; ebahmyari@yahoo.com 2Bs in Electrical Engineering, SPGC; Miri.Hamidreza@spgc.ir 3Bs in Mechanical Engineering, SPGC; Jahankhah.Mostafa@spgc.ir Abstract Inaircoolingrefrigerantcycleswhenairpressureishigherthanrefrigerantpressure,aircanleak through evaporator tubing to the cycle. In this paper first, effects of leaked air into refrigeration cycle is investigated and then amount of air in system is estimated. After that, effects of manual purging of aironthecycleperformanceareinvestigated.Resultsandobservationsshowtheairinthecycle severely decreases heat transfer efficiency of the cycle and life of mechanical elements.Also manual purgingofairfromthecyclecausesrefrigerantlossesthatcontributebothdirectlyandindirectlyto globalwarmingthroughinefficientsystemoperation,increasedpowerconsumptionandgreenhouse gas emissions and higher maintenance costs. Keywords: Air purging; manual purging; air leakage; refrigerant Industrial/Professional Applications Usingwaterwith2barsasmediumfluidforexchangingheatbetweenrefrigerantandaircan prevent leaking air. Air in the cycle increase power consumption and consequently lower cycle performance. Manualpurgingofaircausesrefrigerantlossesthatcontributetoglobalwarmingandcycle performance. Using automatic purger can prevent refrigerant loss and lower maintenance costs in these cases

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1 2 3 4 1 ramin-rabani@stu.yazduni.ac.ir2 vkalantar@yazduni.ac.ir3 mehrdad-rabani@stu.yazduni.ac.ir4 rabaniasd@stu.yazduni.ac.ir

. 1 . ) ( . . . ACH . : . - . 55 80 . ) ( . .

1 Realizable k- Turbulence Model 1114 1 2 1 arashzargar2256@gmail.com2 fj_kazemi@azad.ac.ir

. ISO9806-1 . . . . .

:

- . . Ti-Ta/G . 6128 1 2 1 mr.majdabadi@gmail.com2 - aghanajafi@kntu.ac.ir

. . 90 - 85 . TRNSYS . 48 20 1400 5 ) ( 55 % . . 70 % . :

- . . ) C 90 - 85 ( . 48 20 1400 5 55 % 70 % .

8110 1 21 mr.majdabadi@gmail.com2 aghanajafi@kntu.ac.ir

. 17,5 EES . . 53 % 19 % 6 % .

:

- . 85 0,7 . 8119 GSHP 1 2 1 smehmr@gmail.com 2 javaherdeh@Guilan.ac.ir . . . . . . . : GSHP ) ( R-22 - . . . . 8120

1 2 3 4 1 h_salaryan@yahoo.com2 h.golchoobian@gmail.com3 bahram330ghorbani@gmail.com4 amidpour@kntu.ac.ir

. . . . 52 % 19 % . . . . : .

- . 70 . .8122 1 2 3 1 f_shamsizadeh@yahoo.com2 vkalantar@yazduni.ac.ir3 adehghan@yazduni.ac.ir

12 3 4 . . . 5 6 . SIMPLER . . ACH 9 / 40 % 2 / 76 % .

:

- 30 % . . ACH 9 / 40 % 2 / 76 % .

1 Natural Ventilation 2 Vertical Solar Chimney 3 ACH 4 Flow Pattern 5 Finite Volume Method 6 Pseudo-Transient Approach 8124 1 2 1 rahimi@uma.ac.ir2 Msc.hamedghs@gmail.com

. m 4 m 8 m 100 . . . . . 4 C 12 1700 .

:

- . 2 C 14 . 100 4 1700 . 8125 1 2 3 1 j_pirkandi@dena.kntu.ac.ir2 ghasemi@kntu.ac.ir3 hamedi@kntu.ac.ir

. . . .

:

- . ) 700 1000 ( (CHP) . . . . . . 8139

1 2 1 erfani_83@yahoo.com2 vkalantar@yazduni.ac.ir

1 . 9 4 . 2 . . . . . . . . . 5 . 30 . . . . . :

- . 5 . 2 . .1 unsteady 2 Discrete transfer radiation model (DTRM) 8142 1 2 21 Rezaei.fm@gmail.com2 Bazargan@kntu.ac.ir3 Amidpor@kntu.ac.ir

. . . . .

:

- . ) ( . ) ( .8143

1 2 1 Farzad.Rezvani@hotmail.com2 afnajafi@pwut.ac.ir

m2927 TRANSYS . 1 ) 50 85 ( . . 47 % ) Kwh 49231 ( ) ( m299,6 2) ( 0,62 . 80KW .

: - 20 35 50 ) 20 ( 10 % . 70 / / 0,6 . m299,6 m2927 47 % . 0,62 Kwh 49231 . 1ADsorption chiller 2 Solar fraction 8145 1 2 1 Farzad.Rezvani@hotmail.com2 afnajafi@pwut.ac.ir m2927 . ) 50 85 ( . . 47 % ) Kwh 49231 ( ) ( m2 99,6 . 10 13 .

:

- 20 35 50 10 % . ) 47 % ( m2927 10 13 . ) 70 ( . m2 99,6 /m2 7200000 47 % .1Adsorption chiller 8149

1 2 1 Misagh_moradali@yahoo.com 2 f_jafarkazemi@azad.ac.ir

. 150 . R134a 20 45 . . . . ... . . 45 15 4 / 3 450 5 / 5 950 . . . .

:

- . . . 23 / 6 8 / 6 . 4 / 3 6 . . .

8150 1 21 e.shokoohyan@yahoo.com2 ameri_mm@mail.uk.ac.ir EES . - - . ) ( . . .

: 1 2 3 8154 ) capillary heat exchanger ( 1 2 3 1 hr.hooshangi@gmail.com2 alizadeh@aut.ac.ir3 sepide_njf@yahoo.com . 4 18 - 20 . 4 . . 24 31 .

:

- . 21 . . . ) 3 4 ( . . . . .8157 - 1 2 3 4 1 - poorianaeemi@gmail.com2 - yoonesbayat@yahoo.com3 zamiri_m@nigc-nkgc.ir4 - mahmudgolriz@gmail.com

. . . . . . ... . . . . . . .

: .

- . . . .8160

1 2 3

1 mhmd.ansari@yahoo.com2 arian@ssi.co.ir3 asgharnia_f@yahoo.com

. . . . . . . . . . 20 % 4 % . .

: 1113 1 2 3 4 1 Norouzi@dorsa-group.com2 3 3

. . . . . . .

: DOSG

- 4 . . . DOSG . 5,58 . . DOSG 1 22 . Hypoxia . .

1165 1 2 3 1 ) ( adaneshvar84@gmail.com2 ) ( mir1382@yahoo.com 3 ) ( mkboiler@msa.ir

1 ) AutoCAD ( . ) 2 ( . . . . . ) ( 3 .

- . . . .

1 Fired tube boiler 2 Breathing spac 3 User Friendly 9101 1 2 3 1 ) ( mir1382@yahoo.com2 ) ( adaneshvar84@gmail.com3 ) ( mkboiler@msa.ir . 1 60 100 ) ( . . 50 70 .

:

- . . .1 Combustion chamber 9102