WO2010036540A1 - Augmentation de la capacité pendant la descente - Google Patents
Augmentation de la capacité pendant la descente Download PDFInfo
- Publication number
- WO2010036540A1 WO2010036540A1 PCT/US2009/057068 US2009057068W WO2010036540A1 WO 2010036540 A1 WO2010036540 A1 WO 2010036540A1 US 2009057068 W US2009057068 W US 2009057068W WO 2010036540 A1 WO2010036540 A1 WO 2010036540A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- stages
- refrigerant
- valve
- set forth
- valves
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2507—Flow-diverting valves
Definitions
- This invention relates generally to transport refrigeration systems and, more particularly, to a method for boosting compressor capacity during pulldown operating conditions.
- a second compressor is caused to operate in parallel with the primary compressor to temporarily boost the capacity of the system.
- a two-stage compressor arrangement has a plurality of valves that are operated in such a way as to cause the two-stages to operate in parallel rather than in series operation to thereby boost the capacity of the system.
- FIG. 1 is a schematic illustration of a transcritical refrigeration system with the present invention incorporated therein.
- FIG. 2 is a schematic illustration of one embodiment thereof.
- FIGS. 3 and 4 are a schematic illustrations of another embodiment thereof.
- FIG. 1 Shown in FIG. 1, is a CO 2 refrigerant vapor compression system which includes a primary compression device 11 driven by a motor 12 operatively associated therewith, a refrigerant heat rejecting heat exchanger 13, and a refrigerant heat absorbing heat exchanger 14, also referred to herein as an evaporator, all connected in a closed loop refrigerant circuit in series refrigerant flow arrangement by various refrigerant lines 16, 17 and 18.
- the refrigerant vapor compression system 10 includes a filter drier 19 and a flash tank receiver 21 disposed in refrigerant line 17 of the refrigerant circuit downstream with respect to refrigerant flow of the refrigerant heat rejecting heat exchanger 13 and upstream with respect to refrigerant flow of the evaporator 14, and an evaporator expansion device 22, operatively associated with the evaporator 14, disposed in refrigerant line 17 downstream with respect to refrigerant flow of the flash tank receiver 21 and upstream with respect to refrigerant flow of the evaporator 14.
- the primary compression device 11 functions to compress and circulate CO 2 refrigerant through the refrigerant circuit, and may be a single or a multi-stage compressor such as, for example, a scroll compressor or a reciprocating compressor. In the case of a multiple stage compressor, both compression stages would be driven by the single motor 12 operatively associated in driving relationship with the compression mechanism of the compressor 11.
- the CO 2 refrigerant vapor compression system is designed to operate in a subcritical cycle.
- the refrigerant heat rejecting heat exchanger 13 is designed to operate as a refrigerant condensing heat exchanger through which hot, high pressure refrigerant vapor discharge from the compression device 11 passes in heat exchange relationship with a cooling medium to condense the refrigerant passing therethrough from a refrigerant vapor to refrigerant liquid.
- the refrigerant heat rejecting heat exchanger 13, which may also be referred to herein as a gas cooler or a condenser, may comprise a finned tube heat exchanger, such as, for example, a fin and round tube heat exchange coil or a fin and flat mini-channel tube heat exchanger.
- the typical cooling medium is ambient air passed through the condenser 13 in heat exchange relationship with the refrigerant by means of fan(s) 31 operatively associated with the condenser 13.
- the evaporator 14 constitutes a refrigerant evaporating heat exchanger which, in one form, may be a conventional finned tube heat exchanger, such as, for example, a fin and round tube heat exchange coil or a fin and mini- channel flat tube heat exchanger, through which expanded refrigerant, having traversed the expansion device 22, passes in heat exchange relationship with a heating fluid, whereby the refrigerant is vaporized and typically superheated.
- a conventional finned tube heat exchanger such as, for example, a fin and round tube heat exchange coil or a fin and mini- channel flat tube heat exchanger, through which expanded refrigerant, having traversed the expansion device 22, passes in heat exchange relationship with a heating fluid, whereby the refrigerant is vaporized and typically superheated.
- the heating fluid passed in heat exchange relationship with the refrigerant in the evaporator 14 may be air passed through the evaporator 14 by means of fan(s) 24 operatively associated with the evaporator 14, to be cooled and also commonly dehumidified, and thence supplied to a climate controlled environment which may include a perishable cargo, such as, for example, refrigerated or frozen food items, placed in a storage zone associated with a transport refrigeration system.
- a bypass valve 27 is provided to supplement the refrigerant flow through the expansion device 22 when higher mass flow is required by the refrigeration system. During normal operation, the primary compression device 11 is sufficient to meet the capacity requirements of the system.
- FIG. 2 A control logic diagram is shown in Fig. 2 to illustrate this operation.
- the controller 28 causes the motor 11 to drive the primary compression device 11 only.
- the controller 28 moves to block 36 so as to then operate the motor 29 to drive the booster compressor 31, in parallel with and in addition to the primary compression device 11.
- the control 28 then proceeds to block 33 for normal operation.
- the two-stage compressor is shown generally at 38 and comprises a first stage 39 and a second stage 41.
- a valve 42 is disposed therebetween.
- the valve 42 is open and the two-stage compressor 38 operates as a conventional two-stage compressor.
- valves 43 and 44 which are arranged in parallel relationship with the stage one 39 and stage two 41, respectively.
- the valve 42 is closed and the valves 43 and 44 are opened. The effect is to place the two stages 39 and 41 in parallel relationship as shown in Fig. 4 to thereby temporarily boost capacity of the system.
- the multi-stages compressor can be turned into a regular compressor when the pulldown is achieved or almost achieved, or when the distance between the suction and discharge pressures are too high and causing overheating of the discharge gas.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Le système de réfrigération transcritique est doté d’un compresseur principal et d’un surpresseur qui est conçu pour fonctionner en parallèle avec le compresseur principal seulement dans des conditions de descente. Un seul compresseur à deux étages est doté d'une disposition de soupapes qui est commandée de manière à permettre aux deux étages de fonctionner normalement en série pendant le fonctionnement normal et à permettre le fonctionnement en parallèle dans des conditions de descente.
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2009801381597A CN102165274A (zh) | 2008-09-29 | 2009-09-16 | 降温期间的容量增加 |
EP09816707.5A EP2331887A4 (fr) | 2008-09-29 | 2009-09-16 | Augmentation de la capacite pendant la descente |
US13/061,576 US20110162396A1 (en) | 2008-09-29 | 2009-09-16 | Capacity boosting during pulldown |
JP2011529113A JP2012504221A (ja) | 2008-09-29 | 2009-09-16 | プルダウン時における容量の増加 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10092908P | 2008-09-29 | 2008-09-29 | |
US61/100,929 | 2008-09-29 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010036540A1 true WO2010036540A1 (fr) | 2010-04-01 |
Family
ID=42060045
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2009/057068 WO2010036540A1 (fr) | 2008-09-29 | 2009-09-16 | Augmentation de la capacité pendant la descente |
Country Status (5)
Country | Link |
---|---|
US (1) | US20110162396A1 (fr) |
EP (1) | EP2331887A4 (fr) |
JP (1) | JP2012504221A (fr) |
CN (1) | CN102165274A (fr) |
WO (1) | WO2010036540A1 (fr) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140053585A1 (en) * | 2011-04-21 | 2014-02-27 | Carrier Corporation | Transcritical Refrigerant Vapor System With Capacity Boost |
EP2615392A3 (fr) * | 2012-01-10 | 2016-06-22 | LG Electronics, Inc. | Pompe de chaleur en cascade |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20120282114A1 (en) * | 2011-05-06 | 2012-11-08 | Tonand Brakes Inc. | Air pump |
CN112208293A (zh) * | 2012-09-20 | 2021-01-12 | 冷王公司 | 电动运输制冷系统 |
US20150001849A1 (en) * | 2013-03-07 | 2015-01-01 | Regal Beloit America, Inc. | Energy Recovery Apparatus for a Refrigeration System |
US10543737B2 (en) | 2015-12-28 | 2020-01-28 | Thermo King Corporation | Cascade heat transfer system |
JP6394683B2 (ja) * | 2016-01-08 | 2018-09-26 | 株式会社デンソー | 輸送用冷凍装置 |
US10570783B2 (en) * | 2017-11-28 | 2020-02-25 | Hanwha Power Systems Co., Ltd | Power generation system using supercritical carbon dioxide |
US11209190B2 (en) * | 2019-06-13 | 2021-12-28 | City University Of Hong Kong | Hybrid heat pump system |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5485455A (en) | 1977-12-21 | 1979-07-07 | Mitsubishi Electric Corp | Refrigerating system |
KR20010091850A (ko) * | 2000-03-15 | 2001-10-23 | 가나이 쓰토무 | 냉장고 |
KR20050006002A (ko) * | 2003-07-08 | 2005-01-15 | 삼성전자주식회사 | 냉동시스템 |
US20080226482A1 (en) * | 2005-08-02 | 2008-09-18 | Shanghai Hitachi Electrical Appliances Co., Ltd. | Compressor With Controlled Capacity |
Family Cites Families (23)
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US2154136A (en) * | 1936-03-31 | 1939-04-11 | Carrier Corp | Fluid circulation system |
US4404811A (en) * | 1981-11-27 | 1983-09-20 | Carrier Corporation | Method of preventing refrigeration compressor lubrication pump cavitation |
US4381650A (en) * | 1981-11-27 | 1983-05-03 | Carrier Corporation | Electronic control system for regulating startup operation of a compressor in a refrigeration system |
US5177972A (en) * | 1983-12-27 | 1993-01-12 | Liebert Corporation | Energy efficient air conditioning system utilizing a variable speed compressor and integrally-related expansion valves |
JPS6346350A (ja) * | 1986-08-11 | 1988-02-27 | 株式会社東芝 | 冷凍サイクル |
US4765150A (en) * | 1987-02-09 | 1988-08-23 | Margaux Controls, Inc. | Continuously variable capacity refrigeration system |
JP2541177B2 (ja) * | 1991-02-15 | 1996-10-09 | ダイキン工業株式会社 | 冷凍装置の運転制御装置 |
US5570585A (en) * | 1994-10-03 | 1996-11-05 | Vaynberg; Mikhail | Universal cooling system automatically configured to operate in compound or single compressor mode |
CN1153887A (zh) * | 1995-10-04 | 1997-07-09 | Lg电子株式会社 | 热泵 |
US5768901A (en) * | 1996-12-02 | 1998-06-23 | Carrier Corporation | Refrigerating system employing a compressor for single or multi-stage operation with capacity control |
US5867998A (en) * | 1997-02-10 | 1999-02-09 | Eil Instruments Inc. | Controlling refrigeration |
US6286326B1 (en) * | 1998-05-27 | 2001-09-11 | Worksmart Energy Enterprises, Inc. | Control system for a refrigerator with two evaporating temperatures |
US6460355B1 (en) * | 1999-08-31 | 2002-10-08 | Guy T. Trieskey | Environmental test chamber fast cool down and heat up system |
US6843065B2 (en) * | 2000-05-30 | 2005-01-18 | Icc-Polycold System Inc. | Very low temperature refrigeration system with controlled cool down and warm up rates and long term heating capabilities |
US6619061B2 (en) * | 2001-12-26 | 2003-09-16 | York International Corporation | Self-tuning pull-down fuzzy logic temperature control for refrigeration systems |
JP4018908B2 (ja) * | 2002-01-10 | 2007-12-05 | 株式会社日立製作所 | 冷凍空調装置 |
JP2005001523A (ja) * | 2003-06-12 | 2005-01-06 | Honda Motor Co Ltd | 車両用空調装置 |
US6966192B2 (en) * | 2003-11-13 | 2005-11-22 | Carrier Corporation | Tandem compressors with discharge valve on connecting lines |
JP3984258B2 (ja) * | 2004-12-14 | 2007-10-03 | 三星電子株式会社 | 空気調和機 |
JP2006200820A (ja) * | 2005-01-20 | 2006-08-03 | Sanyo Electric Co Ltd | 太陽光発電装置搭載冷凍車 |
DE102005009173A1 (de) * | 2005-02-17 | 2006-08-24 | Bitzer Kühlmaschinenbau Gmbh | Kälteanlage |
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DE102006050232B9 (de) * | 2006-10-17 | 2008-09-18 | Bitzer Kühlmaschinenbau Gmbh | Kälteanlage |
-
2009
- 2009-09-16 WO PCT/US2009/057068 patent/WO2010036540A1/fr active Application Filing
- 2009-09-16 US US13/061,576 patent/US20110162396A1/en not_active Abandoned
- 2009-09-16 CN CN2009801381597A patent/CN102165274A/zh active Pending
- 2009-09-16 EP EP09816707.5A patent/EP2331887A4/fr not_active Withdrawn
- 2009-09-16 JP JP2011529113A patent/JP2012504221A/ja active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5485455A (en) | 1977-12-21 | 1979-07-07 | Mitsubishi Electric Corp | Refrigerating system |
KR20010091850A (ko) * | 2000-03-15 | 2001-10-23 | 가나이 쓰토무 | 냉장고 |
KR20050006002A (ko) * | 2003-07-08 | 2005-01-15 | 삼성전자주식회사 | 냉동시스템 |
US20080226482A1 (en) * | 2005-08-02 | 2008-09-18 | Shanghai Hitachi Electrical Appliances Co., Ltd. | Compressor With Controlled Capacity |
Non-Patent Citations (1)
Title |
---|
See also references of EP2331887A4 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140053585A1 (en) * | 2011-04-21 | 2014-02-27 | Carrier Corporation | Transcritical Refrigerant Vapor System With Capacity Boost |
US9360237B2 (en) | 2011-04-21 | 2016-06-07 | Carrier Corporation | Transcritical refrigerant vapor system with capacity boost |
EP2615392A3 (fr) * | 2012-01-10 | 2016-06-22 | LG Electronics, Inc. | Pompe de chaleur en cascade |
US9759454B2 (en) | 2012-01-10 | 2017-09-12 | Lg Electronics Inc. | Cascade heat pump |
Also Published As
Publication number | Publication date |
---|---|
CN102165274A (zh) | 2011-08-24 |
EP2331887A4 (fr) | 2013-04-24 |
US20110162396A1 (en) | 2011-07-07 |
EP2331887A1 (fr) | 2011-06-15 |
JP2012504221A (ja) | 2012-02-16 |
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