US20110162396A1 - Capacity boosting during pulldown - Google Patents

Capacity boosting during pulldown Download PDF

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Publication number
US20110162396A1
US20110162396A1 US13/061,576 US200913061576A US2011162396A1 US 20110162396 A1 US20110162396 A1 US 20110162396A1 US 200913061576 A US200913061576 A US 200913061576A US 2011162396 A1 US2011162396 A1 US 2011162396A1
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US
United States
Prior art keywords
stages
refrigerant
valve
set forth
valves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US13/061,576
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English (en)
Inventor
Paul Chen
Bill Bush
Biswajit Mitra
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Priority to US13/061,576 priority Critical patent/US20110162396A1/en
Assigned to CARRIER CORPORATION reassignment CARRIER CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MITRA, BISWAJIT, BUSH, BILL, CHEN, PAUL
Publication of US20110162396A1 publication Critical patent/US20110162396A1/en
Abandoned legal-status Critical Current

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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 perishable cargo such as, for example, refrigerated or frozen food items
  • the expansion device 22 which is normally an electronic expansion valve, operates to control the flow of refrigerant through the refrigerant line 33 to the evaporator 14 in response to the refrigerant suction temperature and pressure sensed by the sensors (not shown) on the suction side of the compression device 11 .
  • 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.
  • FIGS. 3 and 4 another embodiment thereof is shown in FIGS. 3 and 4 , wherein a single, two-stage compressor is operated in such a manner as to perform as a pair of compressors operating in parallel.
  • 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.

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  • 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)
US13/061,576 2008-09-29 2009-09-16 Capacity boosting during pulldown Abandoned US20110162396A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US13/061,576 US20110162396A1 (en) 2008-09-29 2009-09-16 Capacity boosting during pulldown

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US10092908P 2008-09-29 2008-09-29
US13/061,576 US20110162396A1 (en) 2008-09-29 2009-09-16 Capacity boosting during pulldown
PCT/US2009/057068 WO2010036540A1 (fr) 2008-09-29 2009-09-16 Augmentation de la capacité pendant la descente

Publications (1)

Publication Number Publication Date
US20110162396A1 true US20110162396A1 (en) 2011-07-07

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
US13/061,576 Abandoned US20110162396A1 (en) 2008-09-29 2009-09-16 Capacity boosting during pulldown

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 (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120282114A1 (en) * 2011-05-06 2012-11-08 Tonand Brakes Inc. Air pump
US20140053585A1 (en) * 2011-04-21 2014-02-27 Carrier Corporation Transcritical Refrigerant Vapor System With Capacity Boost
US20150001849A1 (en) * 2013-03-07 2015-01-01 Regal Beloit America, Inc. Energy Recovery Apparatus for a Refrigeration System
US20150239324A1 (en) * 2012-09-20 2015-08-27 Thermo King Corporation Electrical transport refrigeration system
US10543737B2 (en) 2015-12-28 2020-01-28 Thermo King Corporation Cascade heat transfer system
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

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101873595B1 (ko) 2012-01-10 2018-07-02 엘지전자 주식회사 캐스케이드 히트펌프 장치 및 그 구동 방법
JP6394683B2 (ja) * 2016-01-08 2018-09-26 株式会社デンソー 輸送用冷凍装置

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US2154136A (en) * 1936-03-31 1939-04-11 Carrier Corp Fluid circulation system
JPS5485455A (en) * 1977-12-21 1979-07-07 Mitsubishi Electric Corp Refrigerating system
US4381650A (en) * 1981-11-27 1983-05-03 Carrier Corporation Electronic control system for regulating startup operation of a compressor in a refrigeration system
US4404811A (en) * 1981-11-27 1983-09-20 Carrier Corporation Method of preventing refrigeration compressor lubrication pump cavitation
US4765150A (en) * 1987-02-09 1988-08-23 Margaux Controls, Inc. Continuously variable capacity 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
US5570585A (en) * 1994-10-03 1996-11-05 Vaynberg; Mikhail Universal cooling system automatically configured to operate in compound or single compressor mode
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
US6536518B2 (en) * 1999-08-31 2003-03-25 Guy T. Trieskey Refrigeration system for an environmental test chamber
US6619061B2 (en) * 2001-12-26 2003-09-16 York International Corporation Self-tuning pull-down fuzzy logic temperature control for refrigeration systems
US20040020221A1 (en) * 2000-05-30 2004-02-05 Flynn Kevin P. Very low temperature refrigeration system with controlled cool down and warm up rates and long term heating capabilities
US20050103037A1 (en) * 2003-11-13 2005-05-19 Alexander Lifson Tandem compressors with discharge valve on connecting lines
US20070240436A1 (en) * 2006-04-03 2007-10-18 Daniel Landers Refrigeration system controller and method
US20080011014A1 (en) * 2005-02-17 2008-01-17 Bitzer Kuhlmaschinenbau Gmbh Refrigeration System
US20080110200A1 (en) * 2006-10-17 2008-05-15 Bitzer Kuehlmaschinenbau Gmbh Refrigerating Plant
US20080226482A1 (en) * 2005-08-02 2008-09-18 Shanghai Hitachi Electrical Appliances Co., Ltd. Compressor With Controlled Capacity

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JPS6346350A (ja) * 1986-08-11 1988-02-27 株式会社東芝 冷凍サイクル
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
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JP4018908B2 (ja) * 2002-01-10 2007-12-05 株式会社日立製作所 冷凍空調装置
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Patent Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2154136A (en) * 1936-03-31 1939-04-11 Carrier Corp Fluid circulation system
JPS5485455A (en) * 1977-12-21 1979-07-07 Mitsubishi Electric Corp Refrigerating system
US4381650A (en) * 1981-11-27 1983-05-03 Carrier Corporation Electronic control system for regulating startup operation of a compressor in a refrigeration system
US4404811A (en) * 1981-11-27 1983-09-20 Carrier Corporation Method of preventing refrigeration compressor lubrication pump cavitation
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
US4765150A (en) * 1987-02-09 1988-08-23 Margaux Controls, Inc. Continuously variable capacity refrigeration system
US5570585A (en) * 1994-10-03 1996-11-05 Vaynberg; Mikhail Universal cooling system automatically configured to operate in compound or single compressor mode
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
US6536518B2 (en) * 1999-08-31 2003-03-25 Guy T. Trieskey Refrigeration system for an environmental test chamber
US20040020221A1 (en) * 2000-05-30 2004-02-05 Flynn Kevin P. 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
US20050103037A1 (en) * 2003-11-13 2005-05-19 Alexander Lifson Tandem compressors with discharge valve on connecting lines
US20080011014A1 (en) * 2005-02-17 2008-01-17 Bitzer Kuhlmaschinenbau Gmbh Refrigeration System
US20080226482A1 (en) * 2005-08-02 2008-09-18 Shanghai Hitachi Electrical Appliances Co., Ltd. Compressor With Controlled Capacity
US20070240436A1 (en) * 2006-04-03 2007-10-18 Daniel Landers Refrigeration system controller and method
US20080110200A1 (en) * 2006-10-17 2008-05-15 Bitzer Kuehlmaschinenbau Gmbh Refrigerating Plant

Cited By (12)

* Cited by examiner, † Cited by third party
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
US20120282114A1 (en) * 2011-05-06 2012-11-08 Tonand Brakes Inc. Air pump
US20150239324A1 (en) * 2012-09-20 2015-08-27 Thermo King Corporation Electrical transport refrigeration system
US9776473B2 (en) * 2012-09-20 2017-10-03 Thermo King Corporation Electrical transport refrigeration system
US10377209B2 (en) 2012-09-20 2019-08-13 Thermo King Corporation Electrical transport refrigeration system
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
US11351842B2 (en) 2015-12-28 2022-06-07 Thermo King Corporation Cascade heat transfer system
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

Also Published As

Publication number Publication date
EP2331887A4 (fr) 2013-04-24
CN102165274A (zh) 2011-08-24
WO2010036540A1 (fr) 2010-04-01
JP2012504221A (ja) 2012-02-16
EP2331887A1 (fr) 2011-06-15

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Owner name: CARRIER CORPORATION, CONNECTICUT

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:CHEN, PAUL;BUSH, BILL;MITRA, BISWAJIT;SIGNING DATES FROM 20091007 TO 20100715;REEL/FRAME:025879/0312

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION