涡旋压缩机英文论文(翻译)
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涡旋压缩机实习报告英文回答:Internship Report on Scroll Compressor.Introduction:During my internship at XYZ Company, I had the opportunity to work with scroll compressors. In this report, I will share my experiences and knowledge gained duringthis period.Description of Scroll Compressor:A scroll compressor is a type of positive displacement compressor that uses two spiral-shaped scrolls to compress the refrigerant or gas. It is widely used in airconditioning systems, heat pumps, and refrigeration systems. The main advantage of a scroll compressor is its high efficiency and low noise level.My Responsibilities:During my internship, I was responsible for assisting the engineers in the assembly and testing of scroll compressors. I learned about the different components of the compressor, such as the fixed scroll, orbiting scroll, and discharge port. I also gained hands-on experience in troubleshooting and maintenance of the compressors.Challenges Faced:One of the challenges I faced was understanding the complex design and operation of the scroll compressor. It took me some time to grasp the concept of how the scrolls interact with each other to compress the gas. However, with the guidance of the engineers and my own research, I was able to overcome this challenge.Learning Experience:Working with scroll compressors has been a valuablelearning experience for me. I have gained a deeper understanding of the principles of thermodynamics and fluid mechanics. I have also learned about the importance of precision and attention to detail in the assembly and testing processes.Example:One of the key lessons I learned was the importance of proper lubrication in scroll compressors. During one of the tests, we noticed that the compressor was making unusual noises. Upon inspection, we found that the lubrication oil level was low. After adding the required amount of oil, the compressor operated smoothly. This experience taught me the significance of regular maintenance and the impact it has on the performance of the compressor.Conclusion:Overall, my internship experience with scroll compressors has been rewarding. I have gained practical knowledge and skills that will be beneficial for my futurecareer in the field of mechanical engineering. I amgrateful for the opportunity to work with experienced professionals and apply theoretical concepts to real-world applications.中文回答:涡旋压缩机实习报告。
谷轮压缩机--中国营销中心:4000-500-856 官网: 谷轮压缩机--中国营销中心 4000-500-856 官网:谷轮压缩机--中国营销中心:4000-500-856 官网:谷轮压缩机--中国营销中心:4000-500-856 官网:1ACopeland is the recognized leader in the development of advanced compressor technology.1B 谷轮压缩机--中国营销中心:4000-500-856 官网:谷轮压缩机--中国营销中心:4000-500-856 官网:2APERFORMANCE NOMINALS50 HERTZR22SINGLE PHASE220-1-50 TEST VOLTAGECAPACITYENERGY EFFICIENCY RATINGRATING MOTOR MODELAMPERESBTU KCAL BTUH KCALH WATTS CONDITIONWATTSWATTSHOURHOURMOTOR WATTS MOTOR WATTSMOTOR WATTSA 183004610536017308.010.6 2.7 3.1ZR22K3-PFJB 182004590533017308.010.5 2.7 3.1C 21500542063001190 5.718.1 4.6 5.3A 204005140598019209.210.6 2.7 3.1ZR24K3-PFJ B 202005090592019209.210.5 2.7 3.1C 24200610070901310 6.318.5 4.7 5.4A 219005520642020109.510.9 2.7 3.2ZR26K3-PFJ B 217005470636020109.510.8 2.7 3.2C 25800650075601400 6.818.4 4.6 5.4A 2380060006970219010.410.9 2.7 3.2ZR28K3-PFJ B 2360059506910219010.410.8 2.7 3.2C 282007110826015107.418.7 4.7 5.5A 2540064007440233011.110.9 2.7 3.2ZR30K3-PFJ B 2520063507380233011.110.8 2.7 3.2C 302007610885016307.918.5 4.7 5.4A 2670067307820243011.811.0 2.8 3.2ZR32K3-PFJ B 2650066807760243011.810.9 2.7 3.2C 315007940923017008.718.5 4.7 5.4A 2830071308290254012.111.1 2.8 3.3ZR34K3-PFJ B 2810070808230255012.111.0 2.8 3.2C 333008390976017308.519.2 4.8 5.6A 3040076608910271013.111.2 2.8 3.3ZR36K3-PFJ B 3020076108850272013.111.1 2.8 3.3C 3600090701050018709.419.3 4.9 5.6A 3360084709840299014.711.2 2.8 3.3ZR40K3-PFJ B 3330083909760300014.711.1 2.8 3.2C 39400993011500207010.819.0 4.8 5.6A 35300890010300314015.211.2 2.8 3.3ZR42K3-PFJ B 35000882010300315015.211.1 2.8 3.3C 415001050012200216010.919.2 4.9 5.6A 38500970011300337016.411.4 2.9 3.4ZR45K3-PFJ B 38200963011200338016.411.3 2.8 3.3C 450001130013200237012.119.0 4.8 5.6A 397001000011600345016.811.5 2.9 3.4ZR47K3-PFJ B 39400993011500346016.811.4 2.9 3.3C 465001170013600242012.619.2 4.8 5.6A 408001030012000362017.611.3 2.8 3.3ZR48K3-PFJ B 405001020011900363017.611.2 2.8 3.3C 478001200014000252013.519.0 4.8 5.6A 575001450016800512024.511.2 2.8 3.3ZR68KC-PFJB 570001440016700513024.511.1 2.8 3.3C673001700019700367018.218.34.65.43BPERFORMANCE NOMINALS50 HERTZR22THREE PHASETEST VOLTAGECAPACITYENERGY EFFICIENCY RATINGRATING MOTOR MODELAMPERES*BTU KCAL BTUH KCALH WATTS CONDITIONWATTSWATTSHOURHOURMOTOR WATTS MOTOR WATTSMOTOR WATTSA 18300461053601770 5.5/3.210.3 2.6 3.0ZR22K3-TF5/DB 18200459053301770 5.5/3.210.3 2.6 3.0C 21500542063001170 4.3/2.518.4 4.6 5.4A 20400514059801920 6.0/3.510.6 2.7 3.1ZR24K3-TF5/DB 20200509059201920 6.0/3.510.5 2.7 3.1C 24200610070901250 4.7/2.719.4 4.9 5.7A 21900552064202010 6.6/3.810.9 2.7 3.2ZR26K3-TF5/DB 21700547063602010 6.6/3.810.8 2.7 3.2C 25800650075601360 5.0/2.919.0 4.8 5.6A 23800600069702150 6.9/4.011.1 2.8 3.2ZR28K3-TF5/DB 23600595069102150 6.9/4.011.0 2.8 3.2C 28200711082601450 5.4/3.119.4 4.9 5.7A 254006400744022907.3/4.211.1 2.8 3.2ZR30K3-TF5/DB 252006350738022907.3/4.211.0 2.8 3.2C 30200761088501540 5.5/3.219.6 4.9 5.7A 267006730782024307.6/4.411.0 2.8 3.2ZR32K3-TF5/DB 265006680776024307.6/4.410.9 2.7 3.2C 31500794092301640 5.9/3.419.2 4.8 5.6A 283007130829025007.9/4.611.3 2.9 3.3ZR34K3-TF5/DB 281007080823025007.9/4.611.2 2.8 3.3C 33400842097901700 6.2/3.619.6 5.0 5.8A 304007660891026908.3/4.811.3 2.8 3.3ZR36K3-TF5/DB 302007610885027008.3/4.811.2 2.8 3.3C 360009070105001810 6.4/3.719.9 5.0 5.8A 336008470984029609.2/5.311.4 2.9 3.3ZR40K3-TF5/DB 333008390976029709.2/5.311.2 2.8 3.3C 3940099301150019907.1/4.119.8 5.0 5.8A 3530089001030031009.5/5.511.4 2.9 3.3ZR42K3-TF5/DB 3500088201030031109.5/5.511.3 2.8 3.3C41500105001220020807.4/4.320.05.05.9*Ampere values shown are at 220 volts/380 volts.220-3-50 (TF5)380-3-50 (TFD)谷轮压缩机--中国营销中心:4000-500-856 官网:谷轮压缩机--中国营销中心:4000-500-856 官网:4A4BPERFORMANCE NOMINALS50 HERTZ R22THREE PHASE TEST VOLTAGECAPACITY ENERGY EFFICIENCY RATINGRATING MOTORMODEL AMPERES*BTU KCAL BTUH KCALH WATTS CONDITION WATTSWATTSHOUR HOUR MOTOR WATTS MOTOR WATTS MOTOR WATTS A38200963011200331010.5/6.111.5 2.9 3.4ZR45KC-TF5/D B37900955011100332010.5/6.111.4 2.9 3.3 C44500112001300022908.3/4.819.4 4.9 5.7A397001000011600342010.9/6.311.6 2.9 3.4ZR47KC-TF5/D B39400993011500343010.9/6.311.5 2.9 3.4 C46300117001360023408.8/5.119.8 5.0 5.8A408001030012000360011.2/6.511.3 2.9 3.3ZR48KC-TF5/D B405001020011900361011.2/6.511.2 2.8 3.3 C47800120001400024908.6/5.019.2 4.8 5.6A454001140013300397012.6/7.311.4 2.9 3.4ZR54KC-TF5/D B450001130013200398012.6/7.311.3 2.8 3.3 C530001340015500282010.0/5.818.8 4.8 5.5A479001210014000416013.5/7.811.5 2.9 3.4ZR57KC-TF5/D B475001200013900417013.5/7.811.4 2.9 3.3 C560001410016400295010.4/6.019.0 4.8 5.6A514001300015100442014.0/8.111.6 2.9 3.4ZR61KC-TF5/D B510001290014900443014.0/8.111.5 2.9 3.4 C600001510017600317011.1/6.418.9 4.8 5.6A580001460017000495014.9/8.611.7 2.9 3.4ZR68KC-TF5/D B575001450016800496014.9/8.611.6 2.9 3.4 C680001710019900343011.4/6.619.8 5.0 5.8A610001540017900517015.4/8.911.8 3.0 3.5ZR72KC-TF5/D B605001520017700518015.4/8.911.7 2.9 3.4 C715001800020900361011.6/6.719.8 5.0 5.8A685001730020100580018.1/10.511.8 3.0 3.5ZR81KC-TF5/D B680001710019900581018.1/10.511.7 2.9 3.4 C795002000023300414015.2/8.819.2 4.8 5.6*Ampere values shown are at 220 volts/380 volts.220-3-50 (TF5) 380-3-50 (TFD)谷轮压缩机--中国营销中心:4000-500-856 官网:谷轮压缩机--中国营销中心:4000-500-856 官网:谷轮压缩机--中国营销中心:4000-500-856 官网:谷轮压缩机--中国营销中心:4000-500-856 官网:谷轮压缩机--中国营销中心:4000-500-856 官网:The bill of material includes features as shown by the X.ACCESSORY INFORMATIONCrankcase Heater - 240 volt - 70 watt 018-0057-00(ZR22 to ZR81)Crankcase Heater - 480 volt - 70 watt 018-0057-01(ZR22 to ZR81)COMPRESSOR OIL CHARGESWHITE OILMMMA POE OILINITIAL REFILL INITIAL REFILL OIL OIL OIL OIL MODELCHARGE CHARGE MODELCHARGE CHARGE OUNCES/LITERSOUNCES/LITERSOUNCES/LITERSOUNCES/LITERSZR22K3ZR22K3E ZR24K33834ZR24K3E 3834ZR26K3 1.12 1.01ZR26K3E 1.12 1.01ZR28K3ZR28K3E ZR30K3ZR32K3ZR30K3E ZR34K3ZR32K3EZR36K34238ZR34K3E 4238ZR40K3 1.24 1.12ZR36K3E 1.24 1.12ZR42K3ZR40K3EZR45K3ZR45KC 4642ZR42K3E 1.36 1.24ZR47K34238ZR47K3E-PFJ 42381.24 1.12 1.24 1.12ZR47KC 4642ZR47KCE-TF5/TFD 46421.36 1.24 1.36 1.24ZR48K34238ZR48K3E-PFJ 42381.24 1.12 1.24 1.12ZR48KC 4642ZR48KCE-TF5/TFD46421.36 1.24 1.36 1.24ZR54KC 6662ZR54KCE 6662ZR57KC 1.95 1.83ZR57KCE 1.951.83ZR61KC ZR61KCE ZR68KC-PFJ 6258ZR68KCE 1.83 1.72ZR68KC-TF5/TFD6056ZR72KCE 60561.77 1.66ZR81KCE1.771.66ZR72KC 6056ZR81KC1.771.66BILL OF MATERIAL PROVISIONSCopeland is pleased to offer the bills of material shown on the previous pages that offer a complete and versa-tile choice to your compressor selection.In addition to the marked features, each compressor will include the following:•Wiring diagram.•Internal line break protector.•Rubber grommet mounting parts with sleeves(kit 527-0116-00).•Grounding tab located in the compressor terminalbox.See outline drawing pages 9B to 11B for stub tube and rotalock connection sizes.谷轮压缩机--中国营销中心:4000-500-856 官网:510-0247-153/4Solder 33/4510-0080-04SUCTIONTABLE BKIT PART NUMBERSUCTION VALVEDISCHARGE VALVE ROTALOCKCONNECTION SIZE IN INCHES AND SEAL PART NUMBERSUGGESTED USAGETYPE ANDVALVE PART NUMBERSIZE IN INCHESSTYLETYPE ANDSIZE IN INCHESSTYLE238.9 - 244.9238.9 - 244.9238.9 - 244.9238.9 - 244.9PERFORMANCE DATA50 HERTZR2220°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR22K3-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)564075709900127001580019500215002360025900120 (48.9)8530111001410017500194002140023500140 (60.0)1200015200170001880020800CAPACITY (KCAL/HOUR)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)142019102490320039804910542059506530120 (48.9)2150280035504410489053905920140 (60.0)30203830428047405240CAPACITY (WATTS)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)165022202900372046305710630069107590120 (48.9)2500325041305130568062706890140 (60.0)35204450498055106090POWER (MOTOR WATTS)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)125012401220122012101190119011801160120 (48.9)1590157015501530152015101500140 (60.0)20301990198019601940ZR22K3-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)5810778010100128001590019500215002360025900120 (48.9)8800113001420017500194002130023400140 (60.0)1200015100168001870020600CAPACITY (KCAL/HOUR)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)146019602550323040104910542059506530120 (48.9)2220285035804410489053705900140 (60.0)30203810423047105190CAPACITY (WATTS)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)170022802960375046605710630069107590120 (48.9)2580331041605130568062406860140 (60.0)35204420492054806040POWER (MOTOR WATTS)°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8200/220-3-50 (TF5)Rated Voltage 220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR22K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)5630758010000129001640020400226002500027600140 (60.0)21302110209020802060ZR22K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)5840767010000130001640020400227002500027500200/220-3-50 (TF5)Rated Voltage220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR24K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)6430872011400146001840022800253002790030800140 (60.0)24002360234023102290ZR24K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)6850882011400146001840022900253002780030600200/220-3-50 (TF5)Rated Voltage220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR26K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)6720917012100155001950024200268002960032700140 (60.0)24602440243024102390ZR26K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)7140922012000154001940024200268002950032400140 (60.0)26202580256025402530Production compressors to meet above nominal performance values within ±5%.200/220-3-50 (TF5)Rated Voltage220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR28K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)76601030013400171002160026800297003290036300140 (60.0)27402700267026502630ZR28K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)7560994013000168002130026500294003240035600140 (60.0)26102590258025602540Production compressors to meet above nominal performance values within ±5%.200/220-3-50 (TF5)Rated Voltage220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)200/220-3-50 (TF5)Rated Voltage220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR30K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8ZR30K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)79801080014200182002290028400314003460038100120 (48.9)11700155001980024800275003040033500140 (60.0)28502800278027602740Production compressors to meet above nominal performance values within ±5%.PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR32K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)84101140015000192002420029900330003640039900140 (60.0)29702940293029102890ZR32K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)80301090014400188002380029700330003640040100140 (60.0)30002950293029002880Production compressors to meet above nominal performance values within ±5%.200/220-3-50 (TF5)Rated Voltage 220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR34K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)91201220016000204002570031900354003920043200140 (60.0)32203170314031203090ZR34K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)89901180015500200002530031500349003850042400140 (60.0)30903070305030303010Production compressors to meet above nominal performance values within ±5%.200/220-3-50 (TF5)Rated Voltage220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR36K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)96901320017200219002740033800374004130045600140 (60.0)33103300329032703250ZR36K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)99001320017100218002730033700374004130045500140 (60.0)32403230322032003180Production compressors to meet above nominal performance values within ±5%.200/220-3-50 (TF5)Rated Voltage220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR40K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)107001440018800240003020037500416004610050800140 (60.0)37803730370036703630ZR40K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)106001390018200235002970037000410004530049800140(60.0)36003570356035303510Production compressors to meet above nominal performance values within ±5%.200/220-3-50 (TF5)Rated Voltage 220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR42K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)115001520019700251003140038800430004740052100140 (60.0)38903850382037903760ZR42K3E-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)115001490019500251003170039100430004720051400140 (60.0)37803750373037003670Production compressors to meet above nominal performance values within ±5%.200/220-3-50 (TF5)Rated Voltage220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR407C20°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR47K3E-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)131001750022500284003530043400480005300058400140 (60.0)43104290429042904300ZR47KCE-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)83201340019300262003430043600488005440060300120 (48.9)3220318031603160317031903220140 (60.0)42704210420041904200Production compressors to meet above nominal performance values within ±5%.200/220-3-50 (TF5)Rated Voltage220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)PERFORMANCE DATA50 HERTZR2220°F (11.1°C) Superheat15°F (8.3°C) Subcooling95°F (35°C) Ambient (Air Over)220/240-1-50 (PFJ) Rated Voltage220-1-50 (PFJ) Test VoltageZR48K3-PFJCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)134001770022800287003560043400478005240057400120 (48.9)20100255003190039100431004740052000140 (60.0)2730033900376004150045700CAPACITY (KCAL/HOUR)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)3380446057507230897010900120001320014500120 (48.9)5070643080409850109001190013100140 (60.0)6880854094801050011500CAPACITY (WATTS)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)39305190668084101040012700140001540016800120 (48.9)58907470935011500126001390015200140 (60.0)80009930110001220013400POWER (MOTOR WATTS)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)239024202440245024602490252025502580120 (48.9)3180317031703170318032003230140 (60.0)42404210420041904190ZR48KC-TF5/TFDCAPACITY (BTU/HOUR)CONDENSING TEMPERATUREEVAPORATING TEMPERATURE °F/°C°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)137001800023000289003570043500478005240057300120 (48.9)20200256003190039100430004730051800140 (60.0)2760034200378004170045800CAPACITY (KCAL/HOUR)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)3450454058007280900011000120001320014400120 (48.9)5090645080409850108001190013100140 (60.0)6960862095301050011500CAPACITY (WATTS)°F/°C – 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)40105270674084701050012700140001540016800120 (48.9)59207500935011500126001390015200140 (60.0)809010000111001220013400POWER (MOTOR WATTS)°F/°C– 10010203040455055– 23.3– 17.8– 12.2– 6.7– 1.1 4.47.210.012.8100 (37.8)233023402350237024102460249025302570120 (48.9)3120311031203150317032003230140 (60.0)41204120412041304150Production compressors to meet above nominal performance values within ±5%.200/220-3-50 (TF5)Rated Voltage 220-3-50 (TF5)Test Voltage380/420-3-50 (TFD)380-3-50 (TFD)。
蒸汽涡轮机英文作文Title: The Steam Turbine - A Pioneering Invention in Energy ConversionThe steam turbine is a remarkable invention that revolutionized the field of energy conversion. This mechanical device extracts energy from pressurized steam and converts it into rotational motion, making it a crucial component in various industrial applications, particularly in power generation.The steam turbine operates on the principle of thermodynamics. Pressurized steam is directed into the turbine, where it expands and rotates the turbine blades. This rotational motion is then harnessed to perform work, such as driving a generator to produce electricity.The efficiency and reliability of the steam turbine have made it a preferred choice in power plants worldwide. Its ability to convert thermal energy into mechanical energy with minimal losses has been a key factor in its widespread adoption. Furthermore, the steam turbine is highly scalable, allowing it to be tailored to meet the specific needs ofdifferent power plants, from small-scale industrial applications to large-scale utility plants.The impact of the steam turbine on society is immense. It has been instrumental in powering industrial revolution, enabling the production of goods and services on an unprecedented scale. Moreover, the widespread use of steam turbines in power generation has contributed to the availability of affordable and reliable electricity, which is crucial for modern society.However, the steam turbine is not without its challenges. The high temperatures and pressures involved in its operation require robust materials and precise engineering. Additionally, the maintenance of steam turbines can be complex and costly.尽管如此,随着technological advancements, the efficiency and durability of steam turbines have been continuously improved, making them more sustainable and cost-effective.In conclusion, the steam turbine stands as a testament to human ingenuity in energy conversion. Its pivotal role in powering industrial revolution and modern society cannot be overstated. With continuous innovation and improvement, the steam turbine remains a crucial component in our energyinfrastructure, driving us towards a brighter and more sustainable future.。
涡旋式压缩机涡旋式压缩机(scroll compressor)是由一个固定的渐开线涡旋盘和一个呈偏心回旋平动的渐开线运动涡旋盘组成可压缩容积的压缩机。
涡旋压缩机的独特设计,使其成为当今世界节能压缩机。
涡旋压缩机主要运行件涡盘只有龊合没有磨损,因而寿命更长,被誉为“免维修压缩机”。
涡旋压缩机运行平稳、振动小、工作环境宁静,又被誉为“超静压缩机”。
涡旋式压缩机结构新颖、精密,具有体积小、噪音低、重量轻、振动小、能耗小、寿命长、输气连续平稳、运行可靠、气源清洁等优点。
涡旋式压缩机工作原理:由一个固定的渐开线涡旋盘和一个呈偏心回旋平动的渐开线运动涡旋盘组成可压缩容积的压缩机。
特点:效率高,更有利于节能,保护环境;噪声更低;体积更小,重量更轻;运行平稳,气流脉动小,扭矩变化小,压缩机寿命长;压缩过程长,相邻压缩腔压差小,泄漏量小,效率更高。
涡旋压缩机的独特设计,使其成为当今世界节能压缩机。
涡旋压缩机主要运行件涡盘只有龊合没有磨损,因而寿命更长,被誉为免维修压缩机。
涡旋压缩机运行平稳、振动小、工作环境宁静,又被誉为‘超静压缩机’。
涡旋式压缩机结构新颖、精密,具有体积小、噪音低、重量轻、振动小、能耗小、寿命长、输气连续平稳、运行可靠、气源清洁等优点。
被誉为‘新革命压缩机’和‘无需维修压缩机’是风动机械理想动力源,广泛运用于工业、农业、交通运输、医疗器械、食品装潢和纺织等行业和其它需要压缩空气的场合。
一种涡旋式压缩机,包括:驱动轴,可向顺时针或逆时针方向进行旋转,并具有既定大小的偏心部;气缸,形成既定大小的内部体积;滚轮,接触于气缸的内周面,并可旋转安装于偏心部的外周面,可沿着内周面进行滚动运动,并与内周面一同形成用于流体的吸入及压缩操作的流体腔室;叶片,弹性安装于气缸,使其与滚轮持续进行接触;上部及下部轴承,它们分别安装在气缸的上下部,用于可旋转支撑上述驱动轴,并封闭内部体积;机油流路,是设置于轴承及驱动轴之间,并使其之间均匀流动有机油;排出端口,它们连通于流体腔室;吸入端口,它们连通于流体腔室,并相互以既定角度进行隔离;阀门组件,它根据驱动轴的旋转方向,而选择性开放各吸入端口中的一个吸入端口。
涡旋式压缩机工作原理
涡旋式压缩机工作原理是通过涡旋(vortex)或称为涡流(swirl)的运动原理来实现气体的压缩。
它将空气或其他气体引入一个筒形腔体,然后以高速旋转的叶轮创造一个旋转的流动场。
涡旋式压缩机的主要组成部分包括一个圆筒形腔体和一个叶轮。
腔体通常是带有入口和出口的环形结构,叶轮则位于腔体内部。
当气体通过入口进入腔体时,叶轮开始转动并产生高速涡旋流动。
在转动的过程中,叶轮的旋转力将气体从腔体底部抬升到腔体顶部,并沿着螺旋形路径流动。
由于旋转速度和叶轮设计的影响,涡旋的速度逐渐增加。
随着气体沿螺旋路径上升,它逐渐被压缩。
当气体到达腔体顶部时,它通过出口被释放出来。
同样,涡旋的运动会带动气体通过出口以较高的速度离开腔体。
通过这种方式,气体被压缩并被释放出来,实现了压缩机的工作。
涡旋式压缩机相比于传统的往复式压缩机具有一些优势。
首先,涡旋式压缩机可以实现较高的压缩比,同时具有较小的尺寸和重量,节省空间。
其次,涡旋式压缩机没有活塞和气缸等运动部件,因此运行更平稳,噪音和振动较低,维护成本更低。
然而,涡旋式压缩机也存在一些限制。
例如,由于旋转叶轮的高速旋转,会产生较高的离心力和摩擦力,导致能量损失和磨
损。
此外,涡旋式压缩机在处理高压和大气流量时可能会出现一些挑战。
总体而言,涡旋式压缩机通过利用涡旋流动的原理来实现气体的压缩,具有一些优势和限制,可广泛应用于许多领域,如制冷、空调、工业气体处理等。
涡旋式汽车空气压缩机的设计与制造艾克考比,JA;伊,OI 生产工程部,贝宁城市大学, 贝宁,尼日利亚摘要:这项工作的重点在于汽车用空调涡旋压缩机的设计制造。
涡旋压缩机是一种容积式压缩机,用两个互相配合的螺旋形涡盘压缩空气。
这是半封闭压缩机的设计,具有噪音小,性能可靠,效率高等优点。
@ 詹姆斯压缩机的主要功能将低压区的液体压缩和输送到高压区(罗杰斯;梅,1994)。
压缩机可分为位移式和涡轮式。
位移型进一步分为往复式和旋转式(可瑞克斯,1995)。
涡旋压缩机是一种新型的旋转式压缩机。
它的排量是靠两个相互啮合的螺旋形涡齿的压缩作用来实现的,其中一个是固定的,而另一个是有其固定轨道的,(安斯赫尔,2004)。
汽车空调系统用的典型的涡旋压缩机主要由以下几部分组成:涡齿,壳体,轴,轴承,冷冻室,橡胶密封件,平衡弹簧,电磁离合器和压力阀,如图6所示现代的涡旋压缩机技术的发展在20世纪70年代,涡旋压缩机的概念是由制冷行业提出来的。
而由他们介绍进入空调行业在上世纪80年代末,涡旋压缩机在住宅和商业应用上取得了广泛的成功。
空调压缩机主要用在小型公寓和车辆系统,如用于加热和冷却的个人家庭或企业热泵系统。
更大的压缩机是在商业领域中的应用,如冷冻机、多种冷凝机组系统。
制冷涡旋压缩机的应用范围很广,包括超市货架,散装牛奶冷却运输货车和海运集装箱等(美国制冷学会,1998;载体,2004)在这种情况下,我们提出了汽车空调涡旋压缩机的设计制造。
而据我所知,目前我们没有国产的压缩机。
致使大量的外汇用于进口它们。
因此,本研究致力于涡旋压缩机的设计和制造技术,以促进我国压缩机技术的发展从而使我们的经济得到改善。
工作原理:压缩过程的设计理念是基于两个相互啮合的涡旋盘压缩使(如图1所示)空气通过旋转轴与电机相连。
上部和下部的涡旋叶片形成新月形的压缩腔。
为降低滚动轨道,密封点在叶片两侧向内移动,推动月牙形的压缩腔向渐开线中心移动。
而随着压缩腔的移动,他们的容积逐渐减少,气体得到压缩(麦卡洛,1979;王;乔培,1994)。
Small COMPRESSORCompressor refrigeration system is the core and heart of its decision to the refrigeration system capabilities and features. This paper not only energy efficient, noise and vibration and refrigeration agent analyzed small refrigeration compressor technical performance, Analysis also have appeared in recent years, the new, special small compressor main feature for us small refrigeration compressor future development trend of laying a technological foundation.As we all know, the compressor refrigeration system is the core and heart. Compressor and decided that the cooling system capacity and features. In a sense, the cooling system design and matching of the compressor is the ability demonstrated. Therefore, countries in the world are all in the refrigeration industry refrigeration compressor research invested a tremendous amount of energy, new research direction, and research results continue to emerge. Compressor technology and performance level with each passing day.1.A compressor Efficiency StudyCompressor refrigeration system is the core energy components, improve the efficiency of refrigeration systems of the most direct and effective means is to increase the efficiency of the compressor, It will bring the energy consumption decreased significantly. Moreover, can only avoid the system take measures (such as simply increasing heat exchanger area, etc.) caused by the consumption of materials increased. In recent years, as world energy shortage situation worsens day by day, more and more attention to various energy-saving work the energy efficiency of products made by the ever-increasing demands. Due to losses such as friction, leakage, harmful heat, the electrical loss, flow resistance, noise vibration of existence, Compressor work far below the actual efficiency of theoretical efficiency. Therefore, from a theoretical point of view, any reduction in a loss of arbitrary measures toimprove the efficiency of the compressor. The objective facts have led to the energy saving compressor scope, direction, width, research topics and results varied.On the current international energy-efficient compressors research concentrated mainly in a few areas : research lubrication properties Compressor parts of the friction bearings to reduce friction characteristics of power, improve the efficiency of the compressor; reduce leakage losses to improve the efficiency of the compressor; using frequency modulation technology or refrigeration system through the effort with the user load to match the best energy saving In this regard the particular frequency technology has been relatively mature well known and not repeat them here. Valve Research is an old topic but it is also an eternal topic, Improvement of the valve designed to improve the efficiency of the compressor also Nagamochi endless harvest. Research in this area many times, from the valve material, sports law, optimizing the structure of the applicable theory, exhaustive testing methods. In short, energy-saving compressors on the research in recent years has become one of the refrigeration industry first hot issues.In recent years, domestic refrigeration compressor industry to studyenergy-saving products are also giving great concern. Progress larger products mainly refrigerator compressor industry. In China efficient refrigerators GEF projects to promote and support, both the enterprises for energy-efficient products is the understanding of the performance of refrigerator compressors have a qualitative leap. At present, domestic enterprises refrigerator compressor products of the highest energy efficiency has reached 1.95%. Refrigerator compressor domestic enterprises to take a lot of technical measures such as high efficiency motors or synchronous motor, concave valves, Plane thrust bearing, low viscosity lubricants, the new Getter muffler, reducing friction losses, and achieved great results. The main problem is the lack of domestic enterprises currently free technology, the technology has to imitate the line mainly, Most of the enterprises to build their own technology infrastructure alsounconscious, nor the interest, and this restricts the development of technological capacity.Relative to the refrigerator compressor industry, domestic energy-efficientair-conditioning compressor study it was not perturbed, Over the years the efficiency of the compressor is no substantive change, greater market demand makes most of the air-conditioning compressor enterprises will concentrate on expanding production on. With the nation on the air conditioner energy efficiency standards set for the further improvement of China's air conditioner exports various perils of showing, domestic air-conditioning compressor of this short-sighted enterprises will be unable to adapt to the energy-saving development of the situation. Enterprise also on the follow-up is weak.2. Compressor noise and vibration studyCurrently, the noise has been regarded as one of the serious pollution. Household refrigeration equipment as the source of power and heart, refrigeration compressor noise, to be a measure of its performance as an important indicator. In fact, to a compressor speaking, Most of the noise is due to shell by some noise from the source excitation (such as springs, refrigerant pressure pulsation, exhaust pipe, lubricants etc. excited). But compressor noise sources and pathways complex and diverse, which gives the compressor noise silencer brought great difficulties.On the compressor noise, vibration and foreign scholars have conducted a large number of long-term research. Here in this regard to the main research results are summarized below :The main refrigeration compressor noise Exaggerative inlet, exhaust radiation aerodynamic noise, mechanical moving parts of machinery noise and noise-driven motor three components :2.1 Aerodynamic noiseCompressor inlet airflow noise is due to the intake manifold pressure pulsation in the elections. Inlet-frequency noise and the intake manifold gas Lane same frequency pulsating with the speed of the compressor. Compressor exhaust noise is due to air in the exhaust pipe caused by fluctuating pressures. Exhaust noise than the inlet noise weak, so the compressor aerodynamic noise generally Inlet mainly noise2.2 Mechanical NoiseCompressor mechanical noise, including members of the general impact and friction, the piston vibration, noise impact of the valve, These noise with randomness, was puted.2.3Electromagnetic noiseCompressor electromagnetic noise is generated by the motor. Motor noise and aerodynamic noise and mechanical noise is weaker compared. Noise source compressor inlet, exhaust, aerodynamic noise, the strongest, followed by mechanical noise and electromagnetic noise. Through in-depth studies, we can further that the main compressor noise from the vibration (from the Department of spring, Refrigeration medium pressure pulsation and smoke exhaust pipe and lubricants have incentive) to the ambient medium spread formation noise. On the effort to reduce compressor noise, much of the literature (abbreviated) proposed a series of measures and the Noise and Vibration Reduction program :① increase rigid shell structure to improve the overall resonance frequency reduces vibration amplitude;② curvature of the shell to avoid mutation, the surface, and the natural frequency is inversely proportional to the radius of curvature. shell shape it should be the smallest curvature radius;③ spring bearing flags will be moved to higher rigid position;④ shell should be used as little as possible of the plane; bending stress and the stress coupling membrane (just on the surface) will shell itself is fairly rigid. Therefore compressor shell to be used as little as possible planar structure;⑤ avoid the exhaust pipe and condenser incentive, optimizing exhaust flow pulsation, Exhaust pipe used in the introduction of additional volume to the elimination of pressure fluctuation spectrum of high-order harmonics;⑥ non-symmetric shell shape; Symmetrical three-dimensional structure means that the axis, along the main axis biggest stress of least resistance. Therefore it is asymmetrical shell structure means that the compressor can be greatly reduced along the axis direction of a force while the probability;⑦ set inlet, exhaust muffler, the closed Compressor Muffler generally muffler. It uses Cross Section, resonant cavity caused acoustic impedance changes in reflectivity or sound energy consumption. or use acoustic-acoustic send phase difference of 180 degrees to offset the muffler of noise. Shell compressor in the lateral closed Unicom a Helmholtz resonator, namely : Helmholtz resonator from the chamber through the neck hole and shell compressor connected into the internal cavity, to reduce compressor cavity stimulated acoustic modal amplitude. The results showed : resonator resonance frequency modulation of the actual compressor cavity stimulated the greatest vibration modes, will be substantially reduced resonance peak response spectrum and lead to significant change. However, it will affect the appearance andthe compressor refrigerator settings, the research results are not yet applied to products.Lubricants and residual volume-coil motor windings will lead to the same types of bulk compressor levels between different (from levels average). By changing the shell external support to increase torsional stiffness and reduce vibration surface; Noise study the complex requirements of researchers has strong theory, the enterprise has good skills base and the need for greater investment and a longer timeframe. This is domestic enterprises compressor one of the weak links, which is now basically in the qualitative phase of experimental research, Along with a great chance and randomness.3. new refrigerants ApplicationBased on the new environmental requirements of refrigerant compressor refrigeration industry is a hot issue. As for the refrigerator product R22 refrigerant substitutes the end of the work, new refrigerant compressor in the past few years mainly concentrated in the air conditioning industry. Apart from the now relatively mature R410A, R407C the study, The largest is the hot issue of CO2 compressor. This is the only issue for a briefing.CO2 currently on the research and application of concentrated mainly in three aspects : one is the most urgent need of alternative refrigerants applications, such as automotive air conditioning, as refrigerant emissions, environmental harm, must be adopted as soon as possible without endangering the environment refrigerants; the other is to consider the characteristics of CO2 cycle, the most favorable to the use of this cycle of occasions, If heat pump water heater is to supercritical CO2 in hot conditions decentralization there is a significant temperature slip will help heat Water heated to a higher temperature characteristics of the focus of public attention; another one is CO2 into account the nature of heat transfer properties and characteristics of using CO2 as a refrigerant, taking into account CO2 good cold flow properties andheat transfer characteristics, use it as a cascade refrigeration cycle cryogenic stage refrigerants.Compressor transcritical carbon dioxide as an air conditioning system efficiency and reliability of the most affected parts, It should be fully integrated supercritical carbon dioxide cycle specific characteristics of a new design. Like ammonia and CO2, the adiabatic exponent K value higher, up 1.30, it may result in the compressor discharge temperature high, However, as the needs of CO2 compressor pressure ratio small, there is no need for cooling the compressor itself. Adiabatic index is high pressure over the small, I can reduce the gap compressor further expansion of the volume losses to the higher volume efficiency compressors. After experimental and theoretical research, Jurgen Horst SUB and found Kruse, reciprocating compressor is a good film sliding seal as the preferred CO2 system. 8:3 its carbon dioxide compressor exhaust valve for improved Exhaust improved compressor efficiency of carbon dioxide increased by 7%.As the carbon dioxide pressure is far greater than the traditional critical circulatory pressure, compressor shaft seal design requirements than the original compressor is much higher, compressor shaft seal leakage over a period of time is still hampered Actually, the main reason.Danfoss, Denso, ZEXEL such as carbon dioxide compressor has entered the stage of small batch production.The IEA in March 1999, the Joint Japan, Norway, Sweden, Britain and the United States to activate the "Selected Issue on CO2 as working fluid Compression Systems in the "three-year project.Beginning in 1994, BMW, DAIMLERBENZ VOL O, Germany's Volkswagen and Danfoss. Péchiney and other European companies launched the famous "RACE"to the joint project, the Joint European well-known universities, automotive air conditioning manufacturers and other developed CO2 automotive air-conditioning system. Subregion Motor Company has production equipment CO2 carair-conditioning systems of cars, Germany KONVECTA production to the quality of CO2 in the air-conditioned Buses run from 1996 to date. DANFOSS, the Obrist Austria, the United Kingdom have developed a carbon dioxide compressor motor. Japan DENSO, ZEXEL CO2 compressor has entered the stage of mass production.With major manufacturers inputs, the type of CO2 compressor with ordinary motor compressor trend line major swing to determine the displacement swashplate, scroll and the main variable displacement.4. New principle of refrigeration compressorsIn recent years, the new structure and working principle of refrigeration compressor made a more progress, mainly linear compressor, Elliptic compressors, compressor rotor Swing, spiral vane compressor, in the past, the author has been described in the article, here will not repeat it.Linear compressor which is the domestic refrigerator compressor industry the focus of attention. In 2004 the International Compressor Engineering Conference has five linear compressor on the article. LG and researchers still Sunpower two main companies. The past two years, several domestic enterprises in the refrigerator compressor to the development of the linear compressor, However, enterprises have the technical foundation for the domestic financial strength and the limitations of scientific research institutions, believe in a short period of time can not enter the stage of industrialization.5 the classification of the refrigeration compressor5.1 reciprocating compressorReciprocating compressor is a kind of traditional refrigeration compressor, the biggest characteristic is to achieve the capacity and pressure than any of the design. Although it is widely applied, but the market share is gradually reduced.So far, the fridge (including small freezing and cold storage device) host compound compressor is ever to give priority to. Through the optimal design of valve structure, friction pair, reciprocating refrigerator compressor refrigeration coefficient of power refrigerating capacity (units) by 1.0 (w/w) of the early ninety s to today's 1.8 or so; In addition to the energy saving technology progress, and environmental protection is closely related to the refrigerant alternative technology has also made gratifying progress, refrigerator system in our country has a large number of using R600 hydrocarbons, such as small refrigeration device is also used the new working substance such as everything. To further improve the efficiency of the reciprocating compressor refrigerator, to reduce the system noise is still the development direction of it.5.2 linear compressorStill make reciprocating linear compressor, due to the linear motion of the motor can be directly drives the piston reciprocating motion, so as to avoid the complexity of the crank connecting rod mechanism and the resulting mechanical power consumption. Linear compressor assembly as the refrigerator system has appeared, the refrigeration coefficient of linear refrigerator compressor has more than 2.0 (w/w), market prospects look good. The main problem is the design of the compressor oil system and the effective control of linear motor displacement limit point and the corresponding anti-collision cylinder technology.5.3 the swash plate compressorSwash plate compressor is also a kind of variant structure of reciprocating compressor, is mainly used in automotive air conditioning system at present. After decades of development, the swash plate compressor has become a very mature model, in possession of more than 70 of the automotive air conditioning compressor market. In spite of this, because it still belongs to the series of reciprocating structure, so in thecar air conditioning system can effect comparing (refrigeration coefficient) and only around 1.5, weight and volume is big, big. Because of the mature of swashplate automobile air conditioning compressor technology, combined with technology, further improvement in the foreseeable future, will continue to maintain a certain market share, but in a certain displacement range by substituting is inevitable.5.4 rotor compressorRotor compressor in the 1970 s by the attention of domestic, it represents the structure including the rolling piston type, sliding-vane, etc. On the rolling piston type is widely used in household air conditioner at present, there are also some applications on the refrigerator. This kind of compressor don't need air suction valve, make it suitable for variable speed operation, which can improve system performance by frequency conversion control. In order to ensure high power (3 p) of the motor output power in the performance of the rolling piston compressor, the domestic research and development and the end of last century, double rotor rolling piston compressor, is now on the market. Double rotor on the rolling piston compressor structure has two advantages: (1) force of the rotating system be improved, the machine vibration and noise is reduced; (2) increase the standalone swept volume and improve the output power of the motor.Below 3 p air conditioning unit, temporarily can not replace a good model of the rolling piston compressor. So improve the efficiency of the compression process, reduce noise and motor speed control and the R410A and other related technical issues after new refrigerating agent, etc., is a research direction of the rolling piston compressor.Sliding vane compressor is a kind of rotor compressor, mainly used to provide compressed air, displacement is in commonly 0.3-3 m3 / min, the market share is low. Rotary vane compressor sliding vane compressor is a kind of transition structure, because of its better starting performance, the compression process torque change is not big, at present is mainly used for miniature cars and some smaller displacementplumbing vehicle air conditioning system. The dynamic characteristics under high speed is the main technology of this compressor research direction.5.5 screw compressorScrew compressor with small size, light weight, easy to maintenance etc., is a model of the fast development in refrigeration compressor. On the one hand, the screw type line, structural design has made considerable progress, on the other hand, the introduction of special screw rotor milling especially grinding, improve the machining precision and machining efficiency of key parts, makes the performance of screw compressor has been effectively improved, industrialization production of the necessary hardware also has the safeguard. At present, the screw compressor is given priority to with compressed air, in medium ReBengShi air conditioning has successful application in the system. Due to increasing the reliability of the screw compressor work within the scope of the medium refrigerating capacity has gradually replace of reciprocating compressor and occupied most of the centrifugal compressor market. 5.6 scroll compressorScroll compressor has been rapid development in the past ten years, the structure of the basic theory, research and development to achieve large-scale industrial production, industrial prototype constitutes the compressor technology development new luminescent spot. The development of numerical control processing technology to realize the mass production, the vortex compressor incomparable performance advantage is the precondition of its vast in the market. A few short years, has been in the field of cabinet air conditioning holds an absolute advantage. In cabinet air conditioning system, scroll compressor refrigeration coefficient has amounted to 3.4 (w/w); In the field of automotive air conditioning, the refrigeration coefficient of scroll compressor has amounted to 2.0 (w/w), and shows strong competition potential. The development of the vortex compressor is to enlarge its range of refrigerating capacity, further improve the efficiency, using alternative working medium and lower the manufacturing cost, etc.Since there is no valve, compression force and torque and small changes in the structure make it more suitable for the advantages of frequency control of motor speed operation, it also become the main direction of scroll compressor technology development. Development of scroll compressor of variable displacement mechanism is the key point of the development of the technology. At present, the use of axial sealing technology, "flexible" theory can realize cooling/heating capacity of 10% to 100% within the scope of the regulation.Due to the vortex compressor suction exhaust characteristic of almost continuous, low starting torque and liquid impact resistance, created the condition for parallel use of vortex compressor. In parallel with the vortex compressor can greatly increase the cooling capacity of the unit, can increase from the current single 25 horsepower to single unit 100 horsepower (4 sets of single parallel), and makes the cold quantity adjustment is more reasonable, give full play to the single machine with the highest efficiency. But single in parallel, one of the biggest problems is the oil return is not the average of the unit when using single machine burning phenomenon.3.1.5 centrifugal compressorAt present in large quantity of cold (greater than 1500 kw) remain within the scope of advantage, this is mainly benefited from the cold quantity range, it has incomparable system overall efficiency. The movement of the centrifugal compressor parts little and simple, and its manufacturing precision is much lower than the screw compressor, these are the characteristics of the manufacturing cost is relatively low, and reliable. Relatively speaking, the development of centrifugal compressor is slow, due to the challenges of the screw compressor and absorption chiller. Centrifuge market capacity is around 700 ~ between 1200, because under the premise that the current technology, the machine is mainly used for air conditioning of large buildings, demand is limited. In recent years because of the large infrastructure projects are built, the centrifugal refrigeration and air conditioning compressor is becoming a hot spot of attention again. Solve surge phenomenon, improve the volume adjustment and theadaptability to change with working condition, miniaturization technology is the main development direction of the centrifugal compressor technology.3.1.6 other structure formsSingle tooth of the compressor, some structures, such as cross slider compressor unique positive displacement compressor also has a certain degree of development, but has not been formed in the domestic production capacity.5. Special refrigeration compressorsAlthough domestic enterprises household refrigeration compressors long accustomed to large-scale production mode, we are accustomed to the number of effectiveness. However, the fierce price competition situation, as products become increasingly lower profit margins, When the production of millions of compressors can only make a few million dollars of profit, some on special refrigeration compressors can be regarded as a way out. Special refrigeration compressor exhaustive, it is impossible in this enumeration. But their common feature is their production scale is small, a single high-profit products faster transition, In most cases the need for the user's requirements designed. These products lead to more and more domestic enterprises to the compressor. If the number of domestic enterprises are developing or already have production capacity of the refrigerator compressor truck翻译小型制冷压缩机研究压缩机是制冷系统的核心和心脏,它决定了制冷系统的能力和特征。
Three-dimension numerical simulation of discharge flow in a scroll air compressorSchool of energy and power engineeringAbstractScroll compressor is being recognized by industry as being high competitive with conventional compressors. Plenty of publications on this subject prove an interest of the researchers as well. Further increases in efficiency may be realized if the flow losses, particularly in the final compression and discharge region are reduced. Detailed understandings of the flow processes occurring in the discharge region are necessary to analysis and reduce the discharge flow losses, which become more serious with operation at large discharge. Due to the complexity of the processes, the only one way to get the results is solving the equations of continuity and momentum using the numerical method. During the past decade, a number of investigations have been conducted on the performance of the scroll compressor. However, relatively little information are available on the details of the fluid flow characteristics within the scroll compressor chamber. In the paper, in the light of the characteristics of a discharge process, reasonable simplification of actual physical model is made and the three-dimension quasi-steady turbulent flow numerical simulation is carried out to study the flow field in the discharge region in a scroll air compressor. Three dimensionaldistributions of velocity and pressure and typical flow patterns that exits in the discharge region are presented, which gives good understanding about the physical processes in the scroll air compressor.1.INTRODUCTIONScroll compressors are applied widely in the refrigeration, air conditioning and power field as being competitive advantages in terms of high efficiency, reduced part requirement, lower noise, and reduced vibration levels. Three exist various losses when a scroll compressor is running, such as moving resistance losses of the orbiting scroll and Oldham, friction losses and flow losses. The discharge flow is the main part of these losses (approximately 3 percent of the input power is consumed due to the flow losses), especially at large discharge . Understanding of the flow processes occurring in the discharge and the final compression region is necessary to reduce these flow losses, which become more pronounced with operation at increasing speed and large discharge. Therefore, three dimension numerical simulation of discharge flow in scroll air compressor with modified top profile is carried out. The important flow patterns that exist in the discharge and final compression region are presented. The analysis results supply the theory basis for finding the sources caused discharge losses and designing the discharge port of scroll compressor, particularly at large discharge.A scroll air compressor of discharge is studied in this paper. The topprofile is modified with symmetrical arcs and the discharge port is kidney-shape port. The basic parameters and modified parameters of scroll tips are shown in the table 1.Figure 1 shows the schematic region of the scroll compressor.Table 1: The basic parameters and modified parameters of scroll tipsFigure 1: Schematic of scroll compressor discharge region.2.PHYSICAL MODELAND AND NUMERICAL METHOD2.1 Physical modelThe gas is driven and compressed by “squish motion” of the orbiting scroll wrap, and this results that an unsteady compressible viscous flow occurs within the scroll compressor working chamber. Due to high rotating speed and steep velocity gradient near the wrap wall, the turbulence characteristics have to be considered. But the orbiting wall speed is small compared to the gas flow velocities, for example, the wall speed is approximately 5 percent of the average velocity of the discharge flow in a scroll air compressor at discharge studied in this paper, so it appears justified that the quasi-steady approach is made to treat the flow field with stationary wall. That is , to ignore the moving of orbiting scroll wall is justified. Therefore, three dimension steady-state turbulence calculations are performed to predict the flow field in the final compressor and discharge region. Air is injected from two sides of thecentral chamber with the instantaneous flow rate at various crank angles. The volume flow rate at various crank angles during the discharge process is shown in figure 2.The figure 3 shows a computational model at a certain crank angle after onset of discharge.Figure 2: V olume flow rate with orbiting discharge crank angleFigure 3: Three dimensional computation model2.2 Numerical methodTurbulent flow exists in the scroll configurations considered and was treated using a normal k- turbulence model. The governing equations were discretized using finite volume method. The SIMPLE algorithm was employed in order to correct the pressure filed. Near the wall, the improved wall function method was employed. The discretization scheme of convection item and diffusion item are respectively the second-order upwind scheme and the central difference scheme. Tao (2001) shows the details of discretization method. In the light of the geometrical characteristics of computational domain, the geometry scale of different parts of the whole domain differs greatly; the block structure gird method was employed to generate grids of the whole domain being separated into several parts, in which grids were generated by the body-fitted coordinate grid system. Grids are so fine that the numerical results are grid-independent. The computational domains at different crank angles are different, so the grids were generated separately. The boundaryconditions are as the followings:(a) InletThe mass flow rate on each of two inlets is the same and equal to the instantaneous volume change rate multiplied by the density.(b)The outlet is set on the location far away as 5 times of height of discharge port in order to guarantee the constant pressure. The discharge pressure is provided on outlet.(c)Non-slip boundary condition for velocity is provided on walls. Advanced wall function method is employed to tread the near wall domain.3. NUMERRICAL RESULTSIn this paper, 0 is defined as the orbiting discharge crank angle. At the discharge moment, that is the crank angle y=45(x is the discharge crank angle), yis taken as zero. Then, y is changing from 0 to 360 degree during the whole process of discharge. According to this definition, for example, at crank angle of 45 degree after the onset of discharge is described as y=45.In this paper, for the convenience of description, location of the z coordinate equal to zero is define as the inlet of discharge port and is named as the surface of the fixed scroll. Location of the z coordinateequal to h (the height of scroll wrap) is named as the top surface of the fixed scroll.The flow field and its discharge from the central chamber region at several crank angles that correspond to 45, 90,180 degree after the onset of discharge is studied. Flow velocity vectors in different axial sections and three dimensional velocity vectors are detailedly analyzed.3.1 y=45The calculated velocity fields in different axial sections are shown in figure 4 (a)-(c) at orbiting discharge crank angle of 45 degree. The flow velocity in fig.4 indicate that flow being injected in the rear of each half central chamber, being turned as it impinges on the opposing wall of orbiting scroll of fixed scroll and proceeding towards the central region of the central chamber. In the central region, flow enters from both half central chamber, passing through throat region formed by the orbiting and fixed scroll tips and proceeds driven by the inertia. Two large scale vortexes develops in the central region near the scroll tips and some small scale vortexes develops in the rear of central chamber near the outer surface of scroll tips. Compared fig 4 (a), (b) with (c), it is shown that vortex flow develops in all different axial sections and number and scale and location of vortex are different in different axial section. That is to say this basic vortex flow pattern persists in this region throughout the entire axial extent of central chamber. Three dimensional velocity vectorsshown in fig 5 indicate clearly the distribution of axial velocity component. The three dimensional flow tends to move vertically downwards as it approaches the central region of the central chamber which is directly upon the discharge port. The axial velocity component is very large at a small axial distance of 0-10mm from the discharge port (when the height of the profile is 52mm). The axial velocity by the order of magnitude is greater than the radial velocity. In contrast, within the rear region of the central chamber, the flow is essentially two dimensional.From the fig 4 and fig 5, it can be seen that the velocity vectors in the mid axial section characterize the general nature of the flow within the entire central chamber. The flow vectors indicate both the two dimensional and the three dimensional nature of the flow depending upon the location. So, only the velocity vectors in the mid plane are analyzed below.Figure 4 : Velocity fields in different axial sectionsFigure 5: Three dimensional velocity vectors3.2 y=90Similar type of flow calculations have been performed at an intermediate crank angle (2=90). It is shown in fig 6. As the discharge process continues in an actual scroll compressor, the orbiting scroll continues to move away from the fixed scroll. This action is associatedwith a progressively increased opening of the central region to the discharge port. This implies a less occluded opening of the discharge port compared with the throat region at y=45.The velocity vectors in axial sections of mid plane and discharge are different from those at y=45 and the magnitude of velocity reduced. A double vortex was predicted to form at the mid axial section and the scale of the vortexes increased to trend to become a large vortex.Figure 6 : Velocity fields in different axial sections3.3 y=180Figure 7 (a)-(b) shows the velocity vectors in the axial sections at orbiting discharge crank angel of 180 degree. From the figure, it is shown that the velocity vectors field is obviously different from those shown in fig .4 and fig.6. A large scale vortex was developed in the discharge region as the discharge port is opened fully. In addition, a less constrictive flow passage exits on the region of the scroll tips, the velocity magnitude reduces further. The velocity vector field shows the occurrence of some small scale vortexes at the rear region of the central chamber.Figure 7: Velocity field in different axial sections4. NONDIMENSIONAL PRESSURE LOSSES COEFFICIENTTo obtain quantitative data characterizing the pressure losses of the final compression and discharge region, nondimensional pressure losses coefficient was define as below:P is the average pressure in the central chamber, pa; pd is the designed discharge pressure, pa.The variation of pressure losses coefficient * with orbiting discharge crank angel for the whole discharge process under different operation conditions is shown in fig 8. the pressure losses coefficient is very large at orbiting discharge crank angel of 0-60 degree. For example, the losses coefficient at 45 degree of orbiting discharge crank angle is approximately ten times larger than the loss coefficient at 180 degree, indicating that the flow losses are largest at the onset of discharge. This result is not surprising, since this is also the point of maximum constriction of the flow area. Furthermore, the high rotating speed and discharge pressure corroborate that significant flow losses would exist. With increasing the opening discharge port, losses coefficient is decreasing rapidly. The results indicate that discharge flow losses concentrate at the onset of discharge and reduce quickly with increasing opening discharge port.In addition, these results imply that the open-close characteristic of discharge port should be stressed to consider when designing a discharge port, particularly for compressor at large discharge. The easier to open, the better the characteristic of discharge port is. Maximum area of discharge port is possibly not the best.Figure 8: Nondimensional pressure losses coefficient with orbitingdischarge crank angle5: CONCLUSIONSInternational Compressor Engineering Conference at Purdue, July 12-15, 2004Three dimension numerical simulation of the discharge flow in a scroll air compressor was conducted to provide the characteristic of flow field in the final compression and discharge region. Detailed analysis is made of the flow velocity vectors in different axial sections. The numerical results show that complex vortex flow patterns exist in the discharge region, not only in axial sections. On the basis of numerical results, the dismensionless pressure losses coefficient is defined and the pressure losses at various crank angles after onset of discharge is analyzed. It is shown that the discharge flow losses greatly large shortly after the onset of discharge. The results shows that, the easier to open, the better the characteristic of discharge port is. Maximum area of discharge port is possibly not the best.REFFRENCES1.Hirano. T., et al., 1989, Development of High Efficiency ScrollCompressor for Heat Pump Air Conditioners, Mitsubishi Heavy Industries, Ltd., Tech. Rev. V ol. 26, No. 3, p: 512-519.2.Patankar S V, Spalding D B., 1972, A calculation procedure forheat、mass and momentum transfer in three-dimensional parabolicflows, Int. J. Heat Transfer, V ol. 15, No.11, p:1787-1806.3.Wang Yunliang, X u zhong, Miao Yongmiao, 1993, Influence ofDifferent Wall Function Methods on turbulent flow fields, Fluid Engineering, V ol. 21, No. 12, : 26-29.4.Tao Wenquan, 2001, Numrical Heat Transfer (second version),Xi’an Jiaotong University Press, Xi’an, 152p.5.Tao Wenquan, 2001, Advanced Numerical Heat Transfer, SciencePublishing Company, Beijing, 41p.6.Thompson J.F., Warsi Z.U.A., Mastin C.W., 1985, Numerical GridGeneration, Foundation and Application, North-Holland New York.。
英文原文1 IntroductionThe screw compressor is one of the most common types of machine used to compress gases. Its construction is simple in that it essentially comprises only a pair of meshing rotors, with helical grooves machined in them, contained in a casing, which fits closely round them. The rotors and casing are separated by very small clearances. The rotors are driven by an external motor and mesh like gears in such a manner that, as they rotate, the space formed between them and the casing is reduced progressively. Thus, any gas trapped in this case is compressed. The geometry of such machines is complex and the flow of the gas being compressed within them occurs in three stages. Firstly, gas enters between the lobes, through an inlet port at one end of the casing during the start of rotation. As rotation continues, the space between the rotors no longer lines up with the inlet port and the gas is trapped and thus compressed. Finally, after further rotation, the opposite ends of the rotors pass a second port at the other end of the casing, through which the gas is discharged. The whole process is repeated between successive pairs of lobes to create a continuous but pulsating flow of gas from low to high pressure.These machines are mainly used for the supply of compressed air in the building industry, the food, process and pharmaceutical industries and, where required, in the metallurgical industry and for pneumatic transport.They are also used extensively for compression of refrigerants in refrigeration and air conditioning systems and of hydrocarbon gases in the chemical industry. Their relatively rapid acceptance over the past thirty years is due to their relatively high rotational speeds compared to other types of positive displacement machine, which makes them compact, their ability to maintain high efficiencies over a wide range of operating pressures and flow rates and their long service life and high reliability. Consequently, they constitute a substantial percentage of all positive displacement compressors now sold and currently in operation.The main reasons for this success are the development of novel rotor profiles, which have drastically reduced internal leakage, and advanced machine tools, which can manufacture the most complex shapes to tolerances of the order of 3 micrometers at an acceptable cost. Rotor profile enhancement is still the most promising means of further improving screw compressors and rational procedures are now being developed both to replace earlier empirically derived shapes and also to vary the proportions of the selected profile to obtain the best result for the application for which the compressor is required. Despite their wide usage, due to the complexity of their internal geometry and the non-steady nature of the processes within them, up till recently, only approximate analytical methods have been available to predict their performance. Thus, although it is known that their elements are distorted both by the heavy loads imposed by pressure induced forces and through temperature changes within them, no methods were available to predict the magnitude of these distortions accurately, nor how they affect the overall performance of the machine. In addition, improved modelling of flow patterns within the machine can lead to better porting design. Also, more accurate determination of bearing loads and how they fluctuate enable better choices of bearings to be made. Finally, if rotor and casing distortion, as a result of temperature and pressure changes within the compressor, can be estimated reliably, machining procedures can be devised to minimise their adverse effects.Screw machines operate on a variety of working fluids, which may be gases, dry vapour or multi-phase mixtures with phase changes taking place within the machine. They may involve oil flooding, or other fluids injected during the compression or expansion process, or be without any form of internal lubrication. Their geometry may vary depending on the number of lobes in each rotor, the basic rotor profile and the relative proportions of each rotor lobe segment. It follows that there is no universal configuration which would be the best for all applications. Hence, detailed thermodynamic analysis of the compression process and evaluation of the influence of the various design parameters on performance is more important to obtain the best results from these machines than from other types which could be used for the same application. A set of well defined criteria governed by an optimisation procedure is therefore a prerequisite for achieving the best design for each application. Such guidelines are also essential for the further improvement of existing screw machine designs and broadening their range of uses. Fleming et al., 1998 gives a good contemporary review of screw compressor modelling, design and application.A mathematical model of the thermodynamic and fluid flow processes within positive displacement machines, which is valid for both the screw compressor and expander modes of operation, is presented in this Monograph. It includes the use of the equations of conservation of mass, momentum and energy applied to an instantaneous control volume of trapped fluid within the machine with allowance for fluid leakage, oil or other fluid injection, heat transfer and the assumption of real fluid properties. By simultaneous solution of these equations, pressure-volume diagrams may be derived of the entire admission, discharge and compression or expansion process within the machine. A screw machine is defined by the rotor profile which is here generated by use of a general gearing algorithm and the port shape and size. This algorithm demonstrates the meshing condition which, when solved explicitly,enables a variety of rotor primary arcs to be defined either analytically or by discrete point curves. Its use greatly simplifies the design since only primary arcs need to be specified and these can be located on either the main or gate rotor or even on any other rotor including a rack, which is a rotor of infinite radius. The most efficient profiles have been obtained from a combined rotor-rack generation procedure.The rotor profile generation processor, thermofluid solver and optimizer,together with pre-processing facilities for the input data and graphical post processing and CAD interface, have been incorporated into a design tool in the form of a general computer code which provides a suitable tool for analysis and optimization of the lobe profiles and other geometrical and physical parameters. The Monograph outlines the adopted rationale and method of modelling, compares the shapes of the new and conventional profiles and illustrates potential improvements achieved with the new design when applied to dry and oil-flooded air compressors as well as to refrigeration screw compressors.The first part of the Monograph gives a review of recent developments in screw compressors.The second part presents the method of mathematical definition of the general case of screw machine rotors and describes the details of lobe shape specification. It focuses on a new lobe profile of a slender shape with thinner lobes in the main rotor, which yields a larger cross-sectional area and shorter sealing lines resulting in higher delivery rates for the same tip speed.The third part describes a model of the thermodynamics of the compression-expansion processes, discusses some modelling issues and compares the shapes of new and conventional profiles. It illustrates the potentialimprovements achievable with the new design applied to dry and oil-flooded air compressors as well as to refrigeration screw compressors. The selection of the best gate rotor tip radius is given as an example of how mathematical modelling may be used to optimise the design and the machine’s operating conditions.The fourth part describes the design of a high efficiency screw compressor with new rotor profiles. A well proven mathematical model of the compression process within positive displacement machines was used to determine the optimum rotor size and speed, the volume ratio and the oil injection position and jet diameter. In addition, modern design concepts such as an open suction port and early exposure of the discharge port were included, together with improved bearing and seal specification, to maximise the compressor efficiency. The prototypes were tested and compared with the best compressors currently on the market. The measured specific power input appeared to be lower than any published values for other equivalent compressors currently manufactured. Both the predicted advantages of the new rotor profile and the superiority of the design procedure were thereby confirmed.1.1 Basic ConceptsThermodynamic machines for the compression and expansion of gases and vapours are the key components of the vast majority of power generation and refrigeration systems and essential for the production of compressed air and gases needed by industry. Such machines can be broadly classified by their mode of operation as either turbomachines or those of the positive displacement type.Turbomachines effect pressure changes mainly by dynamic effects, related to the change of momentum imparted to the fluids passing through them. These are associated with the steady flow of fluids at high velocities and hence these machines are compact and best suited for relatively large mass flow rates. Thus compressors and turbines of this type are mainly used in the power generation industry, where, as a result of huge investment in research and development programmes, they are designed and built to attain thermodynamic efficiencies of more than 90% in large scale power production plant. However, the production rate of machines of this type is relatively small and worldwide, is only of the order of some tens of thousands of units per annum.Positive displacement machines effect pressure changes by admitting a fixed mass of fluid into a working chamber where it is confined and then compressed or expanded and, from which it is finally discharged. Such machines must operate more or less intermittently. Such intermittent operation is relatively slow and hence these machines are comparatively large. They are therefore better suited for smaller mass flow rates and power inputs and outputs. A number of types of machine operate on this principle such as reciprocating, vane, scroll and rotary piston machines.In general, positive displacement machines have a wide range of application, particularly in the fields of refrigeration and compressed air production and their total world production rate is in excess of 200 million units per annum. Paradoxically, but possibly because these machines are produced by comparatively small companies with limited resources, relatively little is spent on research and development programmes on them and there are very few academic institutions in the world which are actively promoting their improvement.One of the most successful positive displacement machines currently in use is the screw or twin screw compressor. Its principle of operation, as indicated in Fig. 1.1, is based on volumetric changes in three dimensions rather than two. As shown, it consists, essentially, of a pair of meshing helical lobed rotors, contained in a casing.The spaces formed between the lobes on each rotor form a series of working chambers in which gas or vapour is contained. Beginning at the top and in front of the rotors, shown in the light shaded portion of Fig. 1.1a, there is a starting point for each chamber where the trapped volume is initially zero. As rotation proceeds in the direction of the arrows, the volume of that chamber then increases as the line of contact between the rotor with convex lobes, known as the main rotor, and the adjacent lobe of the gate rotorFig. 1.1. Screw Compressor Rotorsadvances along the axis of the rotors towards the rear. On completion of one revolution i.e. 360◦by the main rotor, the volume of the chamber is then a maximum and extends in helical form along virtually the entire length of the rotor. Further rotation then leads to reengagement of the main lobe with the succeeding gate lobe by a line of contact starting at the bottom and front of the rotors and advancing to the rear, as shown in the dark shaded portions in Fig. 1.1b. Thus, the trapped volume starts to decrease. On completion of a further 360◦of rotation by the main rotor, the trapped volume returns to zero.The dark shaded portions in Fig. 1.1 show the enclosed region where therotors are surrounded by the casing, which fits closely round them, while the light shaded areas show the regions of the rotors, which are exposed to external pressure. Thus the large light shaded area in Fig. 1.1a corresponds to the low pressure port while the small light shaded region between shaft ends B and D in Fig. 1.1b corresponds to the high pressure port.Exposure of the space between the rotor lobes to the suction port, as their front ends pass across it, allows the gas to fill the passages formed between them and the casing until the trapped volume is a maximum. Further rotation then leads to cut off of the chamber from the port and progressive reduction in the trapped volume. This leads to axial and bending forces on the rotors and also to contact forces between the rotor lobes. The compression process continues until the required pressure is reached when the rear ends of the passages are exposed to the discharge port through which the gas flows out at approximately constant pressure. It can be appreciated from examination of Fig. 1.1, is that if the direction of rotation of the rotors is reversed, then gas will flow into the machine through the high pressure port and out through the low pressure port and it will act as an expander. The machine will also work as an expander when rotating in the same direction as a compressor provided that the suction and discharge ports are positioned on the opposite sides of the casing to those shown since this iseffectively the same as reversing the direction of rotation relative to the ports. When operating as a compressor, mechanical power must be supplied to shaft A to rotate the machine. When acting as an expander, it will rotate automatically and power generated within it will be supplied externally through shaft A.The meshing action of the lobes, as they rotate, is the same as that of helical gears but, in addition, their shape must be such that at any contact position, a sealing line is formed between the rotors and between the rotors and the casing in order to prevent internal leakage between successive trapped passages. A further requirement is that the passages between the lobes should be as large as possible, in order to maximise the fluid displacement per revolution. Also, the contact forces between the rotors should be low in order to minimise internal friction losses.A typical screw rotor profile is shown in Fig. 1.2, where a configuration of 5–6 lobes on the main and gate rotors is presented. The meshing rotors are shown with their sealing lines, for the axial plane on the left and for the cross-sectional plane in the centre. Also, the clearance distribution between the two rotor racks in the transverse plane, scaled 50 times (6) is given above.Fig. 1.2. Screw rotor profile: (1) main, (2) gate, (3) rotor external and (4) pitch circles, (5) sealing line, (6) clearance distribution and (7) rotor flow area between the rotors and housingOil injected Oil FreeFig. 1.3. Oil Injected and Oil Free CompressorsScrew machines have a number of advantages over other positive displacement types. Firstly, unlike reciprocating machines, the moving parts all rotate and hence can run at much higher speeds. Secondly, unlike vane machines, the contact forces within them are low, which makes them very reliable. Thirdly, and far less well appreciated, unlike the reciprocating, scroll and vane machines, all the sealing lines of contact which define the boundaries of each cell chamber, decrease in length as the size of the working chamber decreases and the pressure within it rises. This minimises the escape of gas from the chamber due to leakage during the compression or expansion process.1.2 Types of Screw CompressorsScrew compressors may be broadly classified into two types. These are shown in Fig. 1.3 where machines with the same size rotors are compared:1.2.1 The Oil Injected MachineThis relies on relatively large masses of oil injected with the compressed gas in order to lubricate the rotor motion, seal the gaps and reduce the temperature rise during compression. It requires no internal seals, is simple in mechanical design, cheap to manufacture and highly efficient. Consequently it is widely used as a compressor in both the compressed air and refrigeration industries.1.2.2 The Oil Free MachineHere, there is no mixing of the working fluid with oil and contact between the rotors is prevented by timing gears which mesh outside the working chamber and are lubricated externally. In addition, to prevent lubricant entering the working chamber, internal seals are required on each shaft between the working chamber and the bearings. In the case of process gas compressors, double mechanical seals are used. Even with elaborate and costly systems such as these, successful internal sealing is still regarded as a problem by established process gas compressor manufacturers. It follows that such machines are considerably more expensive to manufacture than those that are oil injected.Both types require an external heat exchanger to cool the lubricating oil before it is readmitted to the compressor. The oil free machine requires an oil tank, filters and a pump to return the oil to the bearings and timing gear.The oil injected machine requires a separator to remove the oil from the high pressure discharged gas but relies on the pressure difference between suction and discharge to return the separated oil to the compressor. Theseadditional components increase the total cost of both types of machine but the add on cost is greater for the oil free compressor.1.3 Screw Machine DesignSerious efforts to develop screw machines began in the nineteen thirties, when turbomachines were relatively inefficient. At that time, Alf Lysholm, a talented Swedish engineer, required a high speed compressor, which could be coupled directly to a turbine to form a compact prime mover, in which the motion of all moving parts was purely rotational. The screw compressor appeared to him to be the most promising device for this purpose and all modern developments in these machines stem from his pioneering work. Typical screw compressor designs are presented in Figs. 1.4 and 1.5. From then until the mid nineteen sixties, the main drawback to their widespread use was the inability to manufacture rotors accurately at an acceptable cost. Two developments then accelerated their adoption. The first was the development of milling machines for thread cutting. Their use for rotor manufacture enabled these components to be made far more accurately at an acceptable cost. The second occurred in nineteen seventy three, when SRM, in Sweden, introduced the “A” profile, which reduced the internal leakage path area, known as the blow hole, by 90%. Screw compressors could then be built with efficiencies approximately equal to those of reciprocating machines and, in their oil flooded form, could operate efficiently with stage pressure ratios of up to 8:1. This was unattainable with reciprocating machines. The use of screw compressors, especially of the oil flooded type, then proliferated.Fig. 1.4. Screw compressor mechanical partsFig. 1.5. Cross section of a screw compressor with gear boxTo perform effectively, screw compressor rotors must meet the meshing requirements of gears while maintaining a seal along their length to minimise leakage at any position on the band of rotor contact. It follows that the compressor efficiency depends on both the rotor profile and the clearances between the rotors and between the rotors and the compressor housing.Screw compressor rotors are usually manufactured on pecialized machines by the use of formed milling or grinding tools. Machining accuracy achievable today is high and tolerances in rotor manufacture are of the order of 5 μm around the rotor lobes. Holmes, 1999 reported that even higher accuracy was achieved on the new Holroyd vitrifying thread-grinding machine, thus keeping the manufacturing tolerances within 3 μm even in large batch production. This means that, as far as rotor production alone is concerned, clearances betweenthe rotors canbe as small as 12 μm.中文译文1 引言螺杆式压缩机是一种最常见的用来压缩气体的机器。
涡旋式压缩机的制作方法涡旋式压缩机(Vortex compressor)是一种基于涡旋流理论的压缩机,通过利用流体在高速旋转时产生的离心力而将气体压缩。
它具有结构简单、体积小、噪声低、维护方便等优点,在空气压缩、制冷和加热、流体输送和振动控制等领域都有广泛的应用。
下面我们来介绍一下涡旋式压缩机的制作方法。
一、设计涡旋式压缩机设计涡旋式压缩机需要掌握涡旋流理论、流体力学、传热学和材料力学等专业知识,并结合实际应用需求进行设计。
以下是设计涡旋式压缩机的一些基本步骤:1. 确定压缩机的工作流量和压缩比。
2. 根据流量和压缩比计算出涡旋室的尺寸和叶片角度等参数。
3. 确定使用的压缩介质和压缩机的材料,并进行强度计算。
4. 在CAD软件中进行三维模型的建立和优化。
二、制作涡旋式压缩机涡旋式压缩机制作一般分为三个步骤:制造涡旋室、制作叶片和组装。
1. 制造涡旋室涡旋室是涡旋式压缩机的核心部件,一般使用不锈钢或铝合金等材料制造。
制造涡旋室需要进行铣削、折弯、焊接等工艺,保证室内的光滑度和密闭性。
2. 制作叶片涡旋式压缩机的叶片对于压缩效率和噪声水平有重要影响。
一般使用铝合金、塑料或树脂等材料制作。
制作过程中需要进行精密的加工,以保证叶片的尺寸和形状准确。
3. 组装涡旋式压缩机的组装需要进行精确定位和调整。
首先将叶片固定在涡旋室壁上,然后将进气口和出气口安装在室壁上,紧密固定并密封,最后进行涡旋室的总体安装,接通电源进行测试。
三、测试和维护涡旋式压缩机的测试和维护是保证其正常工作的重要环节。
在测试过程中需要测试压缩机的流量、压力和效率等指标,确保符合设计要求。
维护过程中主要包括涡旋室的清洗和叶片的更换等,以保证其长期稳定工作。
总之,涡旋式压缩机是目前比较先进的压缩机之一,其制作需要掌握流体力学和材料力学等专业知识,并进行精细加工和高度配合的组装。
涡旋式压缩机的应用广泛,随着技术的不断进步,其在空气压缩、制冷、热力学等领域的应用前景将更加广阔。
外文翻译:Electric automobile air conditioning system trend ofdevelopment1. electric automobile air conditioning systemGlobal warming, air pollution and higher energy costs and other problems have become more severe, as environmental pollution and energy consumption is one of the major sources of energy saving and emission reduction, the problem is more and more extensive attention, governments and automobile enterprises will be energy saving and environmental protection as the future of automotive technology development direction of energy saving and environmental protection, such as the electric emerge as the times require. Electric vehicle is set car technology, electronic and computer technology, electrochemical technology, energy and new materials technology in one of the high-tech products, and common internal combustion engine vehicles, has the advantages of no pollution, low noise and save petroleum resource characteristics. Based on the above electric vehicle characteristics, it is very likely to become the human a new generation of clean environmentally friendly transportation, its popularization has the inestimable significance.Electric vehicle emerged for electric automobile air-conditioning research and development offerred new task and challenge. Automotive air conditioning function is put inside the temperature, humidity, air cleanliness and air flow is maintained in a comfortable state. In various climate conditions, electric car should maintain the comfortable state, to provide a comfortable driving and riding environment. In addition, a set of energy-saving and efficient air conditioning system on electric vehicle market also plays an important role. Therefore, in the development of electric vehicles at the same time, necessary to support the air conditioning system development and research.For the traditional fuel automobile air-conditioning systems, refrigeration mainly uses the engine driven steam compression refrigeration system for cooling and heating, using waste heat from fuel engine. But for the electric automobile in the pure electric vehicles and fuel cell vehicles, no air conditioning compressor engine as power source, also cannot provide as automotive air conditioning heating using heat source in winter, so it cannot be directly using conventional automotive air conditioning system solutions; for hybrid cars, the engine control means diversity, so the air conditioning compressor also cannot use the engine directly driving scheme. Integrated the above reasons, the electric vehicle development process, must study for electric vehicle using a new type of air conditioning system. For electric car,the car has a high voltage DC power supply, therefore, the use of electric heat pump type air conditioning system, compressor with motor direct drive electric vehicle, become feasible solution.2.the characteristics of electric vehicle air conditioningElectric automobile air conditioner and common air conditioning device, electric vehicle air conditioning device and car environment has the following characteristics:①automotive air conditioning system mounted on a moving vehicle, to withstand the severe and frequent vibration and shock, requirements of electric vehicle air conditioning device structure in the various components should have sufficient resistance to vibration and impact strength and good sealing performance of the system;②electric car mostly short distance walking, riding in a relatively short time, plus electric car occupant space ratio, the heat generated is relatively high, relatively large heat load of air conditioning, refrigeration, heating and has the advantages of fast speed ability;③electric automobile air conditioning is the use of the car battery to provide DC power, the working efficiency of the compressor is high, control of high reliability, convenient maintenance;④automobile body heat insulation layer is thin, and doors and windows, large glass area, insulation performance is poor, electric car is no exception, resulting in serious car heat leakage;⑤ inside the facilities is rugged and seat, air distribution organization is difficult, difficult to achieve uniform airflow distribution.3.domestic and international current situation of the development of electric vehicle air conditioning① domestic electric car air-conditioning development statusThe early domestic electric car due to battery capacity constraints, in order not to affect electric vehicle mileage, most electric cars are not equipped with air conditioning system.With the domestic electric car gradually industrialization, marketization, electric vehicles must be equipped with air conditioning system. Due to the unique effects of electric vehicles to electric vehicles, the pure electric vehicles and fuel cell vehicles, no air conditioning compressor engine as power source, also cannot provide as automotive air conditioning heating using heat source in winter, domestic car manufacturers from the traditional fuel automobile air conditioner based onpartial replacement of design, will fuel the engine to drive the the compressor is replaced by a DC motor direct drive compressors, control corresponding change, to complete the refrigeration function, the replacement design effect to resolve the basic problem of electric automobile air-conditioning refrigeration, but the cooling efficiency to be improved. Due to the lack of fuel to the engine waste heat generated by heating, domestic manufacturers mainly use PTC heating and electric heating pipe, the heating mode can meet the heating effect, but these heating mode is hard on the consumption of electric vehicle battery power, the heating efficiency is relatively low, affect electric vehicle mileage.Air conditioning in the selection of the main parts, the current domestic electric car in addition to the compressor and control mode, the other main parts or the use of fuel automotive air conditioning parts, condensing equipment is mainly used to parallel flow condenser, evaporator is mainly used to laminated evaporator, throttle device is still a thermostatic expansion valve, a refrigerant is still R134a.According to the incomplete understanding, the domestic in developing electric vehicle manufacturers such as Chery, BYD,FAW, SAIC, JAC.the current electric vehicle air conditioning facilities basically similar, is in the development present situation.②current situation of the development of foreign electric vehicle air conditioningForeign electric automobile air conditioner development relative to domestic abroad is relatively mature, there is no lack of electric automobile air conditioner with domestic similar patterns, but in the heat pump electric automobile air conditioning already had certain foundation, Japan Honda pure electric cars use electric driven heat pump type air conditioning system, system has a built-in Reverse Converter Control compression pump. In addition, in very cold areas, some type of customers can be optional a fuel heater heating system.Japan electric ( DENSO ) company a few years earlier developed using R134a refrigerant electric car air-conditioning heat pump system, the heat pump system used in the car inside air condenser and evaporator structure. Electric ( DENSO ) Company in 2003also developed as a result of natural refrigerant COgood thermal physical2properties, Denso Japan company for electric car develops a set of COheat pump air2conditioning system, also used in the air duct system is arranged in the2heat exchanger, and R134a system is different when the system for refrigeration mode when the refrigerant flows through the condenser, and internal and external condenser.In order to reduce the air conditioning on battery power consumption, the UnitedStates of America Amerigon company developed air-conditioning seat, the chair is provided with a thermoelectric heat pump, heat pump action is through the need to regulate the temperature in space outside the water tank to transfer heat, thereby realizing the need to regulate the temperature of space refrigeration or heating. This kind of air conditioning seat in addition to energy saving but also can improve the driving, riding comfort, in electric vehicle supporting the use of suitable.Therefore, the foreign electric automobile air conditioner from energy efficient and practical breakthrough, domestic electric car air-conditioning industry should actively to study overseas advanced technology, draw lessons from, and on the basis of innovation breakthrough.4.the development trend of electric vehicle air conditioningElectric automobile driving energy from the battery, which is different from the traditional fuel automobile, made it to the air conditioning system also differed from the fuel of automobile air conditioner, as a drive source of energy for the limited battery capacity, the energy consumption of air conditioning system on electric vehicle mileage has bigger effect. Compared with cars, car air conditioning system energy saving and high efficiency raised taller requirement. At the same time, the electric car air-conditioning refrigeration, heating to solve two problems. According to the electric car special properties, the electric automobile air conditioner using thermoelectric ( I ) air conditioning system and electric heat pump type air conditioning system.1).a thermoelectric ( I ) electric vehicle air conditioning systemThe technology has many suitable for electric vehicles use characteristics, and with the traditional mechanical compression type air conditioning system compared, thermoelectric air conditioning has the following characteristics:① thermoelectric elements work to DC power supply;②change the direction of the current to generate refrigeration, heating the converse effect;③thermoelectric refrigeration piece of thermal inertia is small, cooling time is very short, the hot end heat well cold end load cases, energized in less than a minute, the refrigeration sheet can achieve the maximum temperature difference;④ component for regulating current size can adjust refrigeration speed and temperature, the temperature control precision can reach 0.001℃, and can easily realize the continuous regulating energy;⑤in the correct design and application conditions, the refrigerationefficiency can reach above 90%, and the heating efficiency is greater than 1;⑥ has the advantages of small volume, light weight, compact structure, reduces the electric vehicle kerb mass; high reliability, long service life and convenient maintenance; no moving components, therefore, no vibration, no friction, no noise and impact resistance.2).the heat pump type air conditioning system for electric automobileThe heat pump type air conditioning system on the original fuel car to be improved, the compressor is composed of permanent magnet brushless DC motor for direct drive, the system and the ordinary heat pump air conditioning system have no essential difference, as in electric vehicles, compressor and other major components has its particularity. And foreign heat pump technology has had certain foundation, the biggest advantage is that the refrigeration, heating efficiency is high, relevant enterprise development of full closed electric scroll compressor, is composed of a DC brushless motor drive, through the refrigerant return air cooling, with low noise, small vibration, compact structure, light weight etc.. In the test conditions for the environmental temperature of 40 degrees Celsius, the temperature inside the car is27℃,50% relative humidity conditions, when the system is stable it to1kW energy2.9kW refrigeration quantity; when the environmental temperature is - l0C, the temperature inside the car to25 DEG C,1kW can get the 2.3kW heating energy consumption. In the - l0℃to 40 ℃ under ambient temperature, both with high efficiency for electric vehicles to provide a comfortable driving environment. If the component technology is improved, the corresponding efficiency can also be improved.Based on the above mentioned, from air conditioning technology is mature and the sources of energy to use efficiency comparison, for thermoelectric ( I ) electric vehicle air conditioning system, the existence of thermoelectric materials, figure of merit is low, performance is not ideal, and the thermopile output by constitute a thermoelectric element element yield limit hoof. Does not have the electric automobile air-conditioning energy efficiency requirements. This makes the electric automobile air conditioner are more inclined to use energy efficient heat pump type air conditioner, the technical scheme for different types of motor vehicle has good commonality, and the vehicle structural change is small, is the future development trend of electric vehicle air conditioning.The heat pump type electric automobile air conditioner biggest weakness is the low temperature heating problems, especially in the northeast region, which is also the future of the industry research problem. In order to make the heat pump type electric automobile air conditioner more energy efficient, can from the followingaspects to solve:① to develop more efficient DC scroll compressor;②development control is more accurate, more energy-efficient silicon electronic expansion valve;③ using an efficient parallel flow condenser;④ improve microchannel evaporator structure, so that the refrigerant evaporates more uniform.In addition, the number of electric car door open and in driving by speed, light, speed and other factors, air conditioning heat load. The compressor and the air conditioning system to adapt to the change of condition factors, so the heat pump type air conditioning system for electric automobile variational design is particularly important.电动汽车空调系统发展趋势一、电动汽车空调系统全球气候变暖、大气污染以及能源成本高涨等问题日趋严峻,汽车作为环境污染和能源消耗的主要来源之一,其节能减排问题受到了越来越广泛的重视,各国政府和汽车企业均将节能环保当作未来汽车技术发展的指导方向,这样节能环保的电动也就应运而生。
蒸汽涡轮机英文作文Steam turbines are a type of rotary engine that convert steam energy into mechanical energy. They are widely used in power generation plants, marine propulsion systems, and various industrial applications. The basic principle of a steam turbine involves the expansion ofhigh-pressure steam through a series of stationary nozzles and rotating blades, which in turn causes the rotor to turn and generate mechanical power. Steam turbines offer several advantages, including high efficiency, reliable operation, and the ability to generate large amounts of power. They are commonly used in fossil fuel power plants, nuclear power plants, and renewable energy facilities such as geothermal and solar thermal power plants. Additionally, steam turbines are crucial components in the operation of ships and submarines, where they provide propulsion by rotating the propeller shaft. In industrial settings, steam turbines are utilized in applications such as driving compressors, pumps, and generators. Overall, steam turbines play a significant role in modern society by providing a reliable and efficient source of power generation and mechanical energy.蒸汽涡轮机是一种将蒸汽能转换为机械能的旋转式引擎。
译文:涡旋压缩机涡旋压缩机的运作涡旋压缩机(也叫螺旋式压缩机,涡旋泵,涡旋真空泵)是一个压缩空气或制冷的设备。
它作为汽车增压器(人们熟知的滚动式增压器)和真空泵而用于空气调节设备。
反向操作的涡旋压缩机被称为滚动扩张机,可用于从事流体的扩张机械工作。
许多住宅和热泵中央空调系统和一些汽车空调系统已经采用涡旋压缩机代替了更为传统的旋转式,往复式和摆动板压缩机。
历史:Léon Creux在1905年在法国和美国申请了涡旋压缩机专利(专利号801182)。
Creux最早提出蒸汽机为旋转压缩机的概念,但这一时期的金属铸造技术不够先进,而且要使涡旋压缩机有效发挥作用需要很严格的公差,所以不能兴建工作原型。
第一个可行的涡旋压缩机直到二战结束后才出现在市场上,当时高精密机床刚被获准建设。
它们直到20世纪80年代初才被认为是为空调生产的产品。
设计:涡旋压缩机使用两个交叉滚动到泵,压缩,或施加压力,如液体和气体的流体。
叶片几何可能是渐开线,阿基米德螺旋线,或混合曲线。
通常一个卷轴是固定的,同时其它轨道没有偏心旋转,从而捕捉和抽水或压缩流体之间的滚动槽腔。
另一个产生压缩动作的方法是卷轴共同旋转,虽然作同步运动,但与旋转中心偏移。
如果一个卷轴在轨道上运行,那么相对运动就是一致的。
另一个变化,是灵活的管材如阿基米德螺旋泵作为一个蠕动泵,就像牙膏管一样的原理。
里面填充润滑油,以防止泵管的磨损和外部散热,并使用增强管,通常被称为“软管”。
这种泵类通常被称为一个“软管泵”。
此外,由于没有活动与流体,蠕动泵是制造成本低廉的部件。
他们缺乏阀门,密封件和腺体,使他们保持相对便宜,而一软管或管道的使用使它与其它类型的泵相比保持了低成本的优势。
应用:空调压缩机;真空泵;汽车增压器应用,如大众汽车公司的G - Lader。
相对于其它泵的工程比较与一些传统压缩机的应用相比,这些设备以操作灵活、低噪音、可靠而出名。
不像活塞,在轨道滚动的质量完全可以抵消,质量小可以减少震动。
我和压缩机的故事英语作文In the depths of summer, as the relentless heat enveloped the city, I sought solace within the cool sanctuary of my living room. It was then that I first encountered the enigmatic protagonist of this tale – the compressor.From its hidden abode within the bowels of the air conditioner, the compressor hummed diligently, its rhythmic drone a constant reminder of its tireless efforts to defy the sweltering conditions. Intrigued by this mechanical marvel, I embarked on a journey to unravel its secrets and appreciate its unwavering dedication.The compressor, I discovered, was the heart of the air conditioner, the driving force behind its ability to transform oppressive heat into a refreshing breeze. Its function was deceptively simple yet profoundly impactful –to compress refrigerant gas, raising its pressure and temperature.As I delved deeper into its workings, I marveled at the intricate dance of physics that took place within its metallic chambers. The compressor's piston, driven by an electric motor, moved tirelessly, compressing the refrigerant gas with immense force. This compression forced the gas into a smaller volume, resulting in an increase in both its pressure and temperature.The high-pressure, high-temperature refrigerant gas then embarked on a crucial journey through the condenser coils, where it released its accumulated heat to the surrounding environment. As the gas cooled, it condensed back into a liquid, shedding its thermal burden like a weary traveler.The liquid refrigerant, now at a lower pressure and temperature, continued its odyssey through the expansion valve, where it underwent a dramatic transformation. As it passed through the narrow orifice of the valve, the liquid refrigerant experienced a sudden drop in pressure, causing it to vaporize and expand rapidly.This rapid expansion cooled the refrigerant significantly, creating the icy air that flowed through the evaporator coils and into the living room, banishing the oppressive heat. The cycle then repeated itself, with the compressor relentlessly pumping refrigerant gas, compressing it, and releasing its thermal energy to the outside world, all in the relentless pursuit of cooling comfort.As I spent hours observing the compressor's unwavering operation, I couldn't help but reflect on its parallels to human resilience. Like the compressor, we too areconstantly faced with external pressures and challengesthat threaten to overwhelm us. Yet, just as the compressor tirelessly compresses the refrigerant gas, we must summon our inner strength and determination to overcome the obstacles that life throws our way.The compressor's single-minded focus on its task reminded me of the importance of perseverance and unwavering commitment. No matter how daunting the challenge,we must never lose sight of our goals and continue to push forward, just like the compressor relentlessly pumping refrigerant gas.Moreover, the compressor's ability to transform oppressive heat into refreshing coolness inspired me to believe in the transformative power of adversity. Just as the compressor harnesses the energy of heat to create a cooling breeze, we can harness the challenges we face to grow, adapt, and become stronger.In the end, the compressor became more than just a mechanical device to me. It transformed into a symbol of resilience, determination, and the transformative power of adversity. Its unwavering hum became a soothing reminder that even in the face of oppressive heat, there is always the promise of cooling comfort.And so, as summer waned and the days grew shorter, I bid farewell to my mechanical companion, the compressor. Yet, the lessons I had learned from its unwavering operation would forever remain etched in my memory,inspiring me to face future challenges with renewed strength and unwavering determination.。
涡旋压缩机专业英语A centrifugal compressor is a type of dynamic compressor that utilizes rotating impellers to increase the pressureof a gas by transferring kinetic energy from the rotating impeller to the gas. This process is known as centrifugal force compression. Centrifugal compressors are widely usedin various industries, including oil and gas, petrochemical, power generation, and refrigeration.The main components of a centrifugal compressor include the impeller, the casing, the diffuser, and the inlet guide vanes. The impeller is a rotating component with curved blades that accelerates the gas to high speeds. The casingis a stationary housing that contains the impeller and guides the flow of gas. The diffuser is a stationary component that slows down the high-speed gas and convertsits kinetic energy into pressure. The inlet guide vanes are adjustable vanes located at the inlet of the compressorthat control the flow of gas into the impeller.Centrifugal compressors are classified into two main types: radial and mixed-flow. Radial compressors have a radial flow path, with gas entering and exiting theimpeller in a radial direction. Mixed-flow compressors have a combination of radial and axial flow paths, with gas entering the impeller radially and exiting axially. Mixed-flow compressors are more compact and have higherefficiency compared to radial compressors.One of the key advantages of centrifugal compressors is their ability to handle large volumes of gas at high pressures with relatively low power consumption. They are also known for their smooth and vibration-free operation, making them ideal for applications where noise andvibration are a concern. Additionally, centrifugal compressors are more tolerant to changes in operating conditions compared to other types of compressors, making them versatile and reliable in a wide range of applications.In conclusion, centrifugal compressors are essential equipment in many industries due to their high efficiency, reliability, and versatility. They play a crucial role in various processes, including gas compression, refrigeration, and power generation. With ongoing advancements in technology and design, centrifugal compressors continue to evolve to meet the increasing demands of modern industries.离心式压缩机是一种动力压缩机,利用旋转叶轮将动能从旋转叶轮转移到气体来增加气体的压力。
Chemical and Petroleum Engineering, Vol. 40, Nos. 11–12, 2004COMPRESSORS, PUMPS, REFRIGERATION ENGINEERING UPDATING PISTON PUMPS FOR OILPRODUCTIONB. S. Zakharov,1 G. N. Sharikov,2and E. G. Kormishin2The three-plunger acid treatment pump SIN32 and the two-cylinder double-acting pump NPTs-32 with four working chambers (for cementing units) have been updated to control pump delivery. The fluid delivery diagrams for pumps of various designs are examined and the test results are reported.In drilling and oil production, single-acting three-plunger (triplex) pumps or double-acting two-cylinder (duplex) pumps are used.In injecting reagents (clay drilling mud, water, cement, acid, etc.) into wells, depending on the technology applied,it is required to inject the fluid in amounts ranging from the maximum to the minimum in a single operation. If the bed accepts the injected fluid well, it becomes necessary to maximize pump delivery for quick completion of the operation. If on the other hand, the bed does not accept the fluid well, it becomes necessary to reduce pump delivery so as to restrict the injection pressure to the safe limit. At present, because of wear of well (down-hole) equipment, the permissible injectionpressure is not higher than 10–15 MPa..The delivery of a piston (reciprocating) or a plunger (displacement) type of pump can be controlled in the following ways:• by installing several pumps with identical or different pumping capacities;• by changing the drive rotation speed;• by using cylinders (plungers) of the required size;• by channeling a part of the fluid into a bypass; and• by dismounting one or several valves.The first version is used essentially in drilling. In oil production, generally all versions are used either individually or in some combination.All pumping units designed for injection of various fluids (fluidal materials) for cementing, hydraulic formation fracturing, hydraulic sand-jet flushing of sand bridges, and other flushing operations in oil and gas wells are mounted on the chassis of motor vehicles (trucks), tractors, caterpillar (tracked) carriers, and specially made carriages.The operating parameters of the pumps (delivery and injection pressure) depend on the power of the drive and maximum and minimum speed of the engine and the pump. The pump delivery can be changed by changing the number of pump strokes without stopping the engine with the help of a gearbox (by gear shifting) and with stopping of the engine by installing cylinders of the required size. Replacement of the cylinders takes a lot of time and is not always possible in a continuous echnological process. In the existing pumping plants, the delivery variation range is inadequate. At the minimum rotation speed and cylinder diameter, the delivery remains extremely high, and for injecting the fluid into the bed the pressure has to be raised above what is permissible.Assigned by NGDU Zainskneft’, Ékogermet carried out updating of two types of pumps, namely, SIN32 and NPTs-32.In the three-plunger (triplex) acid treatment pump SIN32, for reducing the minimum delivery down to 1.0 m3/h,plungers having a diameter of 125 mm were replaced with plungers having a diameter of 55 mm. As a result, the theoretical pump delivery was reduced from 16 down to 3.3 m3/h. Further reduction of the pump delivery was achieved by reducing the rotation speed of the vehicle engine to the possible minimum (500–600 rpm).Simultaneously with this, a new design of packing glands (sealing devices) of plungers of the UPN55 type was developed.It was based on Zakharov mechanical seal [1], which demonstrated high reliability and durability in sucker-rod (oil) pumps. The sealing units and the pistons with a diameter of 55 mm were made for the SIN32 pump by ÉLKAMneftemash in Perm. Its finishing and testing were done by Ékogermet jointly with NGDU Zainskneft’.The design of the UPN55-type plunger seal is shown in Fig. 1. The combined seal consists of the main threestage mechanical seal 4 and an elastic sealingcollar 2. Each stage of the mechanical seal consists of ten rings that are elastically pressed against each other and simultaneously against the plunger surface. The rings are pressed against theplunger in pairs from the opposite sides. The next pair is turned relative to the preceding one by 90º. The rings are pressed in the axial direction by rubber rings of round cross section and in the radial direction, by rubber girdles with eccentric collars. The plunger 5 is made of steel 45 and is chromium-plated and the sealing rings are of bronze. Threecartridges with mechanical seals were installed in the housing bore 3 with a clearance that helps self-centering of the seals relative to the plunger. The cartridges are pressed together by a round nut 1 through a bushing with the sealing collar 2. There are holes in the housing for injecting oil and draining out the overflow into the receiving (suction) line of the pump.In contrast to the well-known elastic glands, the mechanical seal does not require periodic adjustments and ensures reliable operation of the assembly over a long period [2]. Use of the updated SIN32 pump having a UPN55 type of mechanical plunger seals confirmed that the proposed design operationally fit.From August through December 2003, NGDU Zainskneft’ carried out s even bottom-hole treatments (BHT) of six wells using the updated SIN32 pump. Different types of technological operations were carried out in the wells: mud acid BHT, muriatic (hydrochloric) acid BHT, injection of the reagents SNPKh-9021, MIAPROM, and RMD, for which SIN32 and ATs-32 pumping units were generally used. If acid or any other reagent could not be forced through (injected) at 12–15 MPa pressure, a low-capacity unit was connected with the SIN32 pump. In that case, the injection pressure dropped by 2–4 MPa。
序号中文英文1空压机Air compressor2压缩机Compressor3活塞式空压机Piston compressor4螺杆式空压机Screw compressor5滑片式空压机Vane compressor6离心式空压机Centrifugal compressor7涡旋式空压机Scroll compressor8无油空压机Oil-free compressor9移动式空压机Portable compressor10喷油螺杆空压机Oil injected screw compressor11储气罐Air Tank12压力表Pressure gauge13油管Oil Tube14风冷却器Air Cooler15油冷却器Oil Cooler16水冷却器Water Cooler17电机Motor18机头Air end19进气阀Inlet valve20温控阀Thermostatic valve21压力传感器Pressure sensor22吸附式干燥机Adsorption drier23冷冻式干燥机Freeze drier24吸附剂Adsorbent25冷煤Refrigerant26过滤器Filter27管路过滤器Pipeline filter28高效过滤器High efficiency air filter 29精密过滤器Fine filter30滤芯Filter element31除尘滤芯Dust removal filter32除油滤芯Oil removal filter33活性碳滤芯Activated carbon filter 34灭菌滤芯Sterilization filter35露点Dew point36压力露点Pressure dew point37自动排水器Automatic drain valve 38电子排水器Electronic drain valve 39智能排水器Intelligent drain valve 40机油Oil41油滤Oil filter42空滤Air filter43空滤总成Air filter housing44油分Air/Oil separator45外置油分Spin-on Air/Oil separator 46法兰Flange47外径Outside diameter48内径Inside diameter49高度Height50跑油Run oil51压差Differential pressure52干燥机Air drier53旋入式过滤器Spin-on Filter54维修包service kit55售后市场after market56压缩空气compressed air57软管Tube58汽水分离器steam separator59油水分离器oil-water separator 60安全芯safe filter61联轴器flex62卸荷阀unloading valve63最小压力阀Min pressure valve 64旁通阀by pass valve65单向阀check valve66替代品replacement67检测阀check valve68垫圈washer69库存store70止动板Lock plate71Motor speed 马达转速zr37vsd(zr45vsd)Delivery air 输送空气压力zr250zr250。
涡旋式汽车空气压缩机的设计与制造艾克考比,JA;伊,OI 生产工程部,贝宁城市大学, 贝宁,尼日利亚摘要:这项工作的重点在于汽车用空调涡旋压缩机的设计制造。
涡旋压缩机是一种容积式压缩机,用两个互相配合的螺旋形涡盘压缩空气。
这是半封闭压缩机的设计,具有噪音小,性能可靠,效率高等优点。
@ 詹姆斯压缩机的主要功能将低压区的液体压缩和输送到高压区(罗杰斯;梅,1994)。
压缩机可分为位移式和涡轮式。
位移型进一步分为往复式和旋转式(可瑞克斯,1995)。
涡旋压缩机是一种新型的旋转式压缩机。
它的排量是靠两个相互啮合的螺旋形涡齿的压缩作用来实现的,其中一个是固定的,而另一个是有其固定轨道的,(安斯赫尔,2004)。
汽车空调系统用的典型的涡旋压缩机主要由以下几部分组成:涡齿,壳体,轴,轴承,冷冻室,橡胶密封件,平衡弹簧,电磁离合器和压力阀,如图6所示现代的涡旋压缩机技术的发展在20世纪70年代,涡旋压缩机的概念是由制冷行业提出来的。
而由他们介绍进入空调行业在上世纪80年代末,涡旋压缩机在住宅和商业应用上取得了广泛的成功。
空调压缩机主要用在小型公寓和车辆系统,如用于加热和冷却的个人家庭或企业热泵系统。
更大的压缩机是在商业领域中的应用,如冷冻机、多种冷凝机组系统。
制冷涡旋压缩机的应用范围很广,包括超市货架,散装牛奶冷却运输货车和海运集装箱等(美国制冷学会,1998;载体,2004)在这种情况下,我们提出了汽车空调涡旋压缩机的设计制造。
而据我所知,目前我们没有国产的压缩机。
致使大量的外汇用于进口它们。
因此,本研究致力于涡旋压缩机的设计和制造技术,以促进我国压缩机技术的发展从而使我们的经济得到改善。
工作原理:压缩过程的设计理念是基于两个相互啮合的涡旋盘压缩使(如图1所示)空气通过旋转轴与电机相连。
上部和下部的涡旋叶片形成新月形的压缩腔。
为降低滚动轨道,密封点在叶片两侧向内移动,推动月牙形的压缩腔向渐开线中心移动。
而随着压缩腔的移动,他们的容积逐渐减少,气体得到压缩(麦卡洛,1979;王;乔培,1994)。
第一轨道开始的两个涡齿的两端完全开放,开始向间隙中充入低压制冷剂气体。
转动的轨道最终闭合制冷剂气体的第一压缩腔。
作为第一个轨道的两端,第一对新月形压缩腔具有向内移动到中间位置,转动的外端开始重新开放接纳更多的低压制冷剂气体。
第二轨道推动第一压缩腔内的气体向涡旋中心移动,不断减小气体的体积和增加气体压力。
第三轨道开始的新月形压缩腔涡旋中心的外面,作为第三轨道继续压缩,叶片的内端断开触点靠近排气孔,第三轨道继续压缩机循环,排出高压制冷气体。
动涡盘的设计图纸,涡旋示于图1-7。
压缩机的参数:轴做的是沿轨道运动的旋转运动,所以必须进行压缩机制平衡配重。
以下是在轴的设计时需要考虑的参数:扭转力矩·轴的直径(D)·剪切应力(τ)·扭转角(θ),允许负载(Fmax),壳体厚Tc轴的设计:轴是设计用来动力传输的,确定一个合适的直径,在操作过程中各种负荷和工作条件下的测定,以确保令人满意的强度和刚度。
轴通常是圆形的横截面可以是空心的或实心的。
在许多标准文本中,阐述了其设计(希格利;米施克,2001厅,等。
2002 可米和格普塔,2005)。
轴做的是沿轨道运动的旋转运动,所以必须进行压缩机制平衡配重。
(投影图如图3所示)。
我们在考虑压缩机轴与叶片的设计时对高压5叶片倾斜72oº角。
图7: 涡旋压缩机的组装图 扭矩:等价于 23.38Nm 轴径: 其中:Kb :疲劳系数应用于弯曲力矩Kt :疲劳系数施加扭转力矩Mb :弯矩Mt :扭矩但轴只有扭转应力和因此KT 是统一的KT = 1 假设KB = 1.5。
从弯矩图计算我们的最大弯矩,允许轴= 37.18nm使用ASME 规范的实心轴方程式。
Mt =23.88Nm 和Mb =37.18Nm得到d= 0.01428 m ,或 d=14.28 mm从轴的ASME 标准尺寸,我们使用轴直径15mm 因此,D = 4×15 = 60 J=1.277x10-6;3.剪应力 (τ 评估值为 : 1.4×105N/m 2;4. 扭转角(θ)=584Mt LGd4 评估值为:0.44°;5. 最大负荷(负荷量)刚度为:F max =3ΔeiL 3 ;其中(转动惯量)= d 464 相当于 2.00×10-9;因此F MAX的评估值为7.8 KN9.30×10-3毫米表1:轴规格特性数值电动机功率(P) 7.50 KW电机的转速(N)3000 rev/min疲劳因素弯矩(KB) 1.50疲劳因素对扭矩(KT) 1.00轮重(W)165.00 N叶片数量 5角(O) 72°张紧力侧(N1) 356.00 N松皮带张力(N2)160.00 N电机的转速(NM)3000 rev/min额定功率(P)7.5 KW单位质量(M)0.12 Kg摩擦系数(F)0.30轴径(D)15.00 mm轴重(WS)9.98 N轴的剪应力(SS) 1.4 x 105 N/m2轴的扭转角(θ)0.440横向刚度(Fmax)7.80 KN轴偏转(Y)9.3x10-3 mm压缩机外壳设计:压缩机壳体在内部压力的影响下有破裂的发展趋势。
这就需要设计的外壳的厚度,以便能承受很高的内部压力,在操作过程中。
套管厚度按C T方程7设计。
腔之间的泄漏室:理想情况下,涡旋压缩机的两个涡盘保持完美的接触旋转,在现实中机器的情况不是这样足够的精确,而是有一个窄窄的间隙。
差距约一微米,这可能会增加磨损或加工不良,它是已知的,如果达到八微米,压缩机就不能正常工作了。
这就是为什么我们要分析流经该间隙,以确定是否泄漏在压缩机相邻的腔室中。
几何原理图参见图8(豪厄尔,2001)。
标准的厚度D和长度L分隔两个压力为P1和P2的相邻腔室。
其中的长度尺度L似乎有点不确定。
采用沿间隙的X和Y方向穿过一个局部坐标系统的方法。
相对于这些坐标表示的底部和顶部涡旋壁(这两者都是随着压缩机旋转)的可压缩流动控制方程---斯托克斯方程其中ρ,U和P代表密度,速度和压力,λ和µ的膨胀系数和剪切粘度和d / dt的比值就是对流导数。
方程(1)代表了质量守恒定律,并且必须以任何速度U和密度ρ的满足,而方程(9)是通常可压缩流体--斯托克斯方程的推广,这是如果你设置为零恢复的点。
在压力∆变化之间的差距,我们可以推导出一个典型的粘性阻力气体流速平衡压力梯度的方程(2)(奥克登,1995)我们可以立即从速度规模中推断出泄漏了一个典型速率U,气体速率的泄露是UD率,所以在一个周期的累计损失通常是UD / W(段伦,等。
1994)我们也比较这一腔原区得到气体的相对损失和泄漏。
表2:泄漏室之间的参数估计财产约值粘度(µ)10-5 kg / m间隙厚度(D)10-6 m接触长度(L)10-2 m旋转频率(W)47.33 s-1压力变化(∆P) 1.60×106 Pa涡旋压缩机腔之间的泄漏估计参数值显示在上面的表2中,相对损失约0.3%,很小,然而,它是明确的,用来增加D.高度敏感的制造工艺:涡旋压缩机的主要部件是曲轴,壳体,轴和压缩室。
涡旋压缩机的其他部分都有橡胶密封件,平衡弹簧;轴承,离合器压力阀等物品。
所以我们有我们的三个主要部分构成:曲轴,外壳和轴,压缩室由于形状复杂。
(剖视图如图2所示)曲轴:加工这些曲轴的钢坯加工成独立的渐开线曲线的形式和约束一个边缘的坚实平台。
曲轴有一个固定件,而其他旋转轨道绕转子中心运动。
这两个元素(在图所示相同的螺旋。
1和9),安装有1800相位差,有防自转机构,在这种情况下,十字滑块联轴器用于确保这些相同的螺旋组装1800相位差。
奥尔德姆联轴器在一个固定角位置上,防止自转同时允许在一个轨道的径向方向上卷轴运动。
轨道运动的幅度依赖于基圆半径和壁厚。
壳体制造方法:用厚度4mm的钢板制造压缩机壳体。
从经济角度我们选择制作加工的车床和焊接的部分。
涡旋压缩机壳体为圆筒形容器垂直分为低压和高压端。
壳体的最大容量是制冷剂吸入压力时。
一个小高压区置于压缩机的静涡盘用来降低气流脉动的声音和振动。
冷制冷剂通过下连接吸入气体进入大吸壳/套管。
气体速度在润滑剂和少量的液体制冷剂作用下从气体中分离时大幅下降。
在涡旋压缩机的吸气时,向上穿过到达曲轴的转子。
油带到压缩机的制冷剂气体夹带的雾量小,提供了必要的涡旋叶片的润滑密封。
压缩气体通过单向阀进入高压腔然后离开压缩机壳体通过排气孔排出。
壳体的下部为油储器。
压缩机高容量储槽能够在长时间运行和大量的制冷剂作用下系统操作。
测试压缩机:装配好的涡旋压缩机,接下来是测试机器能否正常工作。
在以下的观察和试验下完成:。
吸入空气在压力作用进入压缩机。
在出口处的空气量与入口处成正比。
压缩机的主要目的(即增加压力,制冷剂气体温度)实现。
几个测试项目和结果如下表。
初始压力= 1.01×105 N/m2(大气压力)的初始温度为27℃表3:试验结果系列号输出压力(N/m2) 输出温度(°C)效率%实验1 1.42 x 105 57.60 63.73实验2 1.37 x 105 54.20 56.67实验3 1.65 x 105 71.80 93.33实验4 1.62 x 105 70.20 90.00实验5 1.59 x 105 68.10 85.63然后,相应的平均效率为77.88%讨论:设计概念是基于两个互相配合的涡旋盘通过曲轴与皮带轮的帮助,从电动机通过皮带驱动压缩机。
机器的尺寸是根据严格的计算的。
今天,世界上使用汽车空调涡旋压缩机的都是小尺寸。
制冷气体的压力进入压缩机决定压缩机出口的压力大小。
结论:我们在这项工作中,提出了涡旋压缩机的设计制造。
本机(压缩机)有助于压缩进入车辆空调系统的冷凝器的空气,然后到接收器,膨胀阀,蒸发器。
压缩机运行效率为77.88%。
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