WO2006101566A1 - Regulation de haute pression pour compression de vapeur transcritique - Google Patents

Regulation de haute pression pour compression de vapeur transcritique Download PDF

Info

Publication number
WO2006101566A1
WO2006101566A1 PCT/US2005/047528 US2005047528W WO2006101566A1 WO 2006101566 A1 WO2006101566 A1 WO 2006101566A1 US 2005047528 W US2005047528 W US 2005047528W WO 2006101566 A1 WO2006101566 A1 WO 2006101566A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
compressor
flow path
refrigerant
expansion device
Prior art date
Application number
PCT/US2005/047528
Other languages
English (en)
Inventor
Tobias H. Sienel
Yu Chen
Original Assignee
Carrier Commercial Refrigeration, Inc.
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 Commercial Refrigeration, Inc. filed Critical Carrier Commercial Refrigeration, Inc.
Priority to JP2008501866A priority Critical patent/JP2008533428A/ja
Priority to CN200580049138XA priority patent/CN101142450B/zh
Priority to US11/908,629 priority patent/US20080202140A1/en
Priority to EP05856008A priority patent/EP1963760A4/fr
Publication of WO2006101566A1 publication Critical patent/WO2006101566A1/fr
Priority to HK08109821.8A priority patent/HK1118600A1/xx

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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2600/17—Control issues by controlling the pressure of the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/02—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors plug-in type
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D31/00—Other cooling or freezing apparatus
    • F25D31/006—Other cooling or freezing apparatus specially adapted for cooling receptacles, e.g. tanks
    • F25D31/007—Bottles or cans

Definitions

  • the invention relates to refrigeration. More particularly, the invention relates to beverage coolers.
  • FIG. 1 schematically shows transcritical vapor compression system 20 utilizing CO 2 as working fluid.
  • the system comprises a compressor 22, a gas cooler 24, an expansion device 26, and an evaporator 28.
  • the exemplary gas cooler and evaporator may each take the form of a refrigerant-to-air heat exchanger. Airflows across one or both of these heat exchangers may be forced. For example, one or more fans 30 and 32 may drive respective airflows-34 and 36 across the two heat exchangers.
  • a refrigerant flow path 40 includes a suction line extending from an outlet of the evaporator 28 to an inlet 42 of the compressor 22.
  • a discharge line extends from an outlet 44 of the compressor to an inlet of the gas cooler. Additional lines connect the gas cooler outlet to expansion device inlet and expansion device outlet to evaporator inlet.
  • COP Coefficient of Performance
  • An electronic expansion valve is usually used as the device 26 to control the high side pressure to optimize the COP of the CO 2 vapor compression system.
  • An electronic expansion valve typically comprises a stepper motor attached to a needle valve to vary the effective valve opening or flow capacity to a large number of possible positions (typically over one hundred). This provides good control of the high side pressure over a large range of operating conditions.
  • the opening of the valve is electronically controlled by a controller 50 to match the actual high side pressure to the desired set point.
  • This pressure control strategy involves a fairly high cost valve, a sophisticated controller 50, and a sensor 52 for measuring the high side pressure. This equipment adds a significant amount of cost to the CO 2 vapor compression system, causing the CO 2 vapor compression system to be less attractive compared to an HFC system.
  • a fixed expansion device e.g., a fixed orifice or capillary tube
  • a fixed expansion device can work well to regulate the system high side pressure to a near optimum pressure.
  • the flowrate through a fixed speed and displacement compressor high flowrate can cause the high side pressure to exceed a safe limit.
  • An expensive expansion device may be eliminated in favor of a less expensive pressure regulator in a CO 2 vapor compression system such as is used in a bottle cooler or small-capacity air conditioner, refrigerator, or other system.
  • the potential for overpressurization may be reduced by using an inexpensive, multi-step fixed expansion device based on one or more solenoid valves.
  • FIG. 1 is a schematic of a prior art vapor compression system.
  • FIG.2 is a schematic of a first inventive CO 2 vapor compression system.
  • FIG. 3 is a schematic of a second inventive CO 2 vapor compression system.
  • FIG.4 is a schematic of a third inventive CO 2 vapor compression system.
  • FIG. 5 is a schematic of a fourth inventive CO 2 vapor compression system.
  • FIG. 6 is a schematic of a fifth inventive CO 2 vapor compression system.
  • FIG. 7 is a schematic of a sixth inventive CO 2 vapor compression system.
  • FIG. 8 is a schematic of a seventh inventive CO 2 vapor compression system.
  • FIG. 9 is a side schematic view of a display case including a refrigeration and air management cassette.
  • FIG. 10 is a view of a refrigeration and air management cassette.
  • the current invention relates to high-side pressure optimization for a CO 2 vapor compression system.
  • a fixed expansion device e.g., an orifice or capillary tube
  • the preset value should be determined such that the CO 2 vapor compre'ssfon systen ⁇ c'fflSbM&ve the best overall Coefficient of Performance (COP) for the entire operating envelope.
  • COP Coefficient of Performance
  • the compressor flowrate will be significantly higher than during steady state conditions.
  • the high-side pressure should be optimized such that the pulldown cooling capacity of the CO 2 vapor compression system can be maximized, but the flow through the pressure regulator does not exceed the flow through the compressor (so that the system pressure becomes too great).
  • This optimal high-side pressure for maximizing capacity is usually higher than the optimal high-side pressure for maximizing the overall COP.
  • the expansion device may be configured to have a larger flow capacity during pulldown conditions. A simple multi-position expansion device may provide this. There are a number of ways through which this can be achieved through the use of solenoid valves to enable a two or more position pressure control system.
  • FIG. 2 shows a system 60 in which the refrigerant flow path 62 is split into two parallel branches/segments 64 and 66 between the gas cooler 24 outlet and evaporator 28 inlet.
  • the first branch 64 has a first fixed expansion device 68.
  • the second branch 66 includes, in series, a solenoid valve 70 and a second fixed expansion device 72.
  • the solenoid valve 70 is shown upstream of the second fixed expansion device 72, this order may be reversed.
  • the exemplary solenoid valve 70 has two settings/conditions. One setting/condition is a fully closed condition in which no flow may pass along the second branch 66.
  • the second setting/condition is a fully open condition allowing flow to pass through the second branch 66 with a minimal pressure loss across the solenoid valve 70.
  • FIG. 3 shows a system 80 wherein the refrigerant flow path 82 has two segments/branches 84 and 86 in parallel upstream of a first fixed expansion device 88.
  • the first branch 84 includes a solenoid valve 90.
  • the second branch 86 includes a second fixed expansion device 92.
  • the solenoid valve 90 is closed to prevent flow along the first branch 84.
  • the second branch 86 acts as a bypass with restricted flow passing through the second fixed expansion device 92 before then passing through the first fixed expansion device 88.
  • the solenoid valve 90 is open, allowing an essentially unrestricted flow along the first branch 84.
  • FIG. 4 shows another system 100 wherein the flow path 102 has first and second segments/branches 104 and 106 between the gas cooler and evaporator.
  • a fixed expansion device 108 is located in the first branch 104.
  • a solenoid valve 110 is located in the second branch 106. The solenoid valve 110 combines aspects of a solenoid valve and a fixed expansion device.
  • FIG. 5 shows a branch-less system 120 in which, along the flow path 122, a solenoid valve 124 and fixed expansion device 126 are located in series.
  • the solenoid valve 124 combines aspects of the solenoid valve and a fixed expansion device differently from the valve 110 of FIG. 4.
  • the valve element (e.g., the solenoid plunger) of the solenoid valve 124 may have a small orifice so that its closed condition is only a partially closed condition.
  • the open condition is an essentially fully open condition with low pressure drop. " Accordingly, during steady state operating conditions, the solenoid valve
  • FIG. 6 shows a system 140 combining aspects of the systems 80 and 120. Specifically, the flow path 142 has two segments/branches 144 and 146 in parallel upstream of a first fixed expansion device 148. The first branch 144 includes a solenoid valve 150. The second branch 146 includes a fixed expansion device 152.
  • the exemplary solenoid valve 150 may, similar to the solenoid valve 124, have a closed condition that is only partially closed. During pulldown conditions, the solenoid valve 150 is open. During steady state conditions, the valve 150 is closed. In the steady state condition, there is a relatively small flow along each of the branches. During pulldown conditions, a larger flow may pass along the first branch 144, with a residual flow along the second branch 146.
  • FIG. 7 shows another system 160 wherein the flow path 162 includes a solenoid valve 164 that combines solenoid valve and orifice functions. Specifically, the element of the solenoid valve 144 includes an orifice so that the closed condition is only partially closed. During steady state conditions, the valve 144 is in its closed condition with the orifice passing the relatively small flow. During pulldown conditions, the valve is open so that a larger flow is passed.
  • FIG. 8 shows a system 180 wherein the flow path 182 includes segments/branches 184 and 186 between the gas cooler and the evaporator.
  • a solenoid valve 188 and 190 is located in each of the branches.
  • the elements of these solenoid valves may include orifices. Independent control over the valves may provide more than two alternative effective flow restrictions. For example, with different size orifices, the two valves provide up to four different effective restrictions.
  • a minimal restriction may be present with both valves open.
  • a maximal restriction may be present with both valves closed.
  • a pair of intermediate restrictions may be achieved with one of the valves closed and the other open.
  • the conduit of the branches may be sized or the valve sized or additional restriction may be present so that with only one valve open there is not essentially free flow.
  • An alternative embodiment could feature such valves in series rather than parallel.
  • a variety of sensor and/or user inputs may be used to control the solenoid valve(s).
  • Direct measurement of the high-side pressure may be made by the sensor 74. When this pressure exceeds one or 'more associated thresholds, the controller 76 may cause the valve(s) to assume an associated relatively free-flow condition.
  • input may be received from an air temperature sensor.
  • the exemplary sensor 75 may be positioned to be exposed to air in or from the cooler interior (e.g., to the flow 36 upstream of the evaporator 28). The sensor 75 may form part of a control thermostat. Accordingly, use of such a sensor alone may permit cost savings through the elimination of the pressure sensor 52 or 74.
  • the flow through the system is a direct function of the density of the refrigerant entering the compressor and, to a lesser extent, the pressure ratio of the compressor.
  • the inlet density is a direct function of the saturation temperature and superheat of the refrigerant.
  • These, in turn, are direct functions of the air temperature, system size, and charge.
  • these parameters may be determined in the design stage as a function of air temperature flowing through the evaporator. A correlation can be produced which matches the evaporator air temperature to the refrigerant inlet density.
  • the solenoid valve(s) would remain in the open position until the output of the evaporator temperature sensor 75 drops below a predetermined value.
  • the solenoid valve or one of the solenoid valves is closed. This can be repeated for systems having multiple solenoid valves further reducing the effective expansion orifice area as the temperature drops so as to maintain a mere optimal pressure in the high pressure portion of the system.
  • FIG. 9 shows an exemplary cooler 200 having a removable cassette 202 containing the refrigerant and air handling systems.
  • the exemplary cassette 202 is mounted in a compartment of a base 204 of a housing.
  • the housing has an interior volume 206 between left and right side walls, a rear wall/duct 216, a top wall/duct 218, a front door 220, and the base compartment.
  • the interior contains a vertical array of shelves 222 holding beverage containers 224.
  • the exemplary cassette 202 draws the air flow 34 through a front grille in the base 224 and discharges the air flow 34 from a rear of the base.
  • the cassette may be extractable through the base front by removing or opening the grille.
  • the exemplary cassette drives the air fbw " 3 ⁇ 3 on a recifculatmg'flow path through the interior 206 via the rear duct 210 and top duct 218.
  • FIG. 10 shows further details of an exemplary cassette 202.
  • the heat exchanger 28 is positioned in a well 240 defined by an insulated wall 242.
  • the heat exchanger i28 is shown positioned mostly in an upper rear quadrant of the cassette and oriented to pass the air flow 36 generally rearwardly, with an upturn after exiting the heat exchanger so as to discharge from a rear portion o the cassette upper end.
  • a drain 250 may extend through a bottom of the wall 242 to pass water condensed from the flow 36 to a drain pan 252.
  • a water accumulation 254 is shown in the pan 252.
  • the pan 252 is along an air duct 256 passing the flow 34 downstream of the heat exchanger 24. Exposure of the accumulation 254 to the heated air in the flow 34 may encourage evaporation.

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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)

Abstract

Selon l'invention, un dispositif d'expansion coûteux peut être remplacé par un régulateur de pression moins coûteux dans un système de compression de vapeur de CO2, tel que celui utilisé dans un refroidisseur de bouteilles ou un climatiseur de faible capacité, un réfrigérateur ou un autre système.
PCT/US2005/047528 2005-03-18 2005-12-30 Regulation de haute pression pour compression de vapeur transcritique WO2006101566A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
JP2008501866A JP2008533428A (ja) 2005-03-18 2005-12-30 遷臨界蒸気圧縮システムの高圧側圧力調整
CN200580049138XA CN101142450B (zh) 2005-03-18 2005-12-30 跨临界制冷***
US11/908,629 US20080202140A1 (en) 2005-03-18 2005-12-30 High Side Pressure Regulation For Transcritical Vapor Compression System
EP05856008A EP1963760A4 (fr) 2005-03-18 2005-12-30 Regulation de haute pression pour compression de vapeur transcritique
HK08109821.8A HK1118600A1 (en) 2005-03-18 2008-09-04 A transcritical refrigeration system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US66396005P 2005-03-18 2005-03-18
US60/663,960 2005-03-18

Publications (1)

Publication Number Publication Date
WO2006101566A1 true WO2006101566A1 (fr) 2006-09-28

Family

ID=37024108

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2005/047528 WO2006101566A1 (fr) 2005-03-18 2005-12-30 Regulation de haute pression pour compression de vapeur transcritique

Country Status (6)

Country Link
US (1) US20080202140A1 (fr)
EP (1) EP1963760A4 (fr)
JP (1) JP2008533428A (fr)
CN (1) CN101142450B (fr)
HK (1) HK1118600A1 (fr)
WO (1) WO2006101566A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2310773A4 (fr) * 2008-06-30 2014-01-01 Carrier Corp Systeme de boitier d'affichage de refroidissement a distance

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1963763A4 (fr) * 2005-03-18 2010-09-29 Carrier Comm Refrigeration Inc Transfert thermique a eau condensee pour systeme de refrigeration a dioxyde de carbone transcritique
CN101413748A (zh) * 2007-10-17 2009-04-22 开利公司 整机展示柜***
WO2010039630A2 (fr) * 2008-10-01 2010-04-08 Carrier Corporation Régulation de pression côté haute pression pour système frigorifique transcritique
CA2771113A1 (fr) * 2012-03-08 2012-05-22 Serge Dube Systeme de refrigeration au co2 pour surfaces de sport sur glace
US9546807B2 (en) * 2013-12-17 2017-01-17 Lennox Industries Inc. Managing high pressure events in air conditioners
CN111351273A (zh) * 2020-04-13 2020-06-30 宁波奥克斯电气股份有限公司 一种节流机构、空调器及节流控制方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3774406A (en) * 1971-11-01 1973-11-27 Singer Co Condensate collector pan heating
JPH01275219A (ja) * 1988-04-28 1989-11-02 Sanden Corp 車両用冷蔵冷房装置
US6105386A (en) * 1997-11-06 2000-08-22 Denso Corporation Supercritical refrigerating apparatus
US6584796B2 (en) * 2000-10-20 2003-07-01 Denso Corporation Heat pump cycle having internal heat exchanger
EP1462740A2 (fr) 2003-03-24 2004-09-29 Sanyo Electric Co., Ltd. Réfrigérateur
US6848268B1 (en) * 2003-11-20 2005-02-01 Modine Manufacturing Company CO2 cooling system

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4332138A (en) * 1979-08-08 1982-06-01 Tokyo Shibaura Denki Kabushiki Kaisha Refrigerating apparatus
US4340404A (en) * 1979-10-01 1982-07-20 Tokyo Shibaura Denki Kabushiki Kaisha Refrigerating apparatus
US4835977A (en) * 1983-11-18 1989-06-06 Teledyne Industries, Inc. Apparatus and method of air-conditioning parked aircraft
KR200144985Y1 (ko) * 1997-05-21 1999-06-15 최진호 쇼케이스의 제상수 배수장치
DE19832479A1 (de) * 1998-07-20 2000-01-27 Behr Gmbh & Co Mit CO¶2¶ betreibbare Klimaanlage
JP2000046420A (ja) * 1998-07-31 2000-02-18 Zexel Corp 冷凍サイクル
DE19852127B4 (de) * 1998-11-12 2008-09-11 Behr Gmbh & Co. Kg Expansionsorgan und hierfür verwendbare Ventileinheit
JP2000179460A (ja) * 1998-12-15 2000-06-27 Denso Corp 圧縮機
US6289930B1 (en) * 1999-07-23 2001-09-18 Ward J. Simon Refrigerant expansion device having combined piston orifice valve and solenoid-actuated closure
US6418735B1 (en) * 2000-11-15 2002-07-16 Carrier Corporation High pressure regulation in transcritical vapor compression cycles
JP3728592B2 (ja) * 2001-02-14 2005-12-21 株式会社日立製作所 空気調和機
JP2003322274A (ja) * 2002-04-26 2003-11-14 Tgk Co Ltd 電磁制御弁
JP4090317B2 (ja) * 2002-09-25 2008-05-28 株式会社テージーケー 電磁弁付膨張弁
JP2004156823A (ja) * 2002-11-06 2004-06-03 Matsushita Refrig Co Ltd 冷却システム
JP4307878B2 (ja) * 2003-03-24 2009-08-05 三洋電機株式会社 冷媒サイクル装置
US20050172654A1 (en) * 2003-11-20 2005-08-11 Hussmann Corporation Modular refrigeration unit
US7165412B1 (en) * 2004-11-19 2007-01-23 American Power Conversion Corporation IT equipment cooling

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3774406A (en) * 1971-11-01 1973-11-27 Singer Co Condensate collector pan heating
JPH01275219A (ja) * 1988-04-28 1989-11-02 Sanden Corp 車両用冷蔵冷房装置
US6105386A (en) * 1997-11-06 2000-08-22 Denso Corporation Supercritical refrigerating apparatus
US6584796B2 (en) * 2000-10-20 2003-07-01 Denso Corporation Heat pump cycle having internal heat exchanger
EP1462740A2 (fr) 2003-03-24 2004-09-29 Sanyo Electric Co., Ltd. Réfrigérateur
US6848268B1 (en) * 2003-11-20 2005-02-01 Modine Manufacturing Company CO2 cooling system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1963760A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2310773A4 (fr) * 2008-06-30 2014-01-01 Carrier Corp Systeme de boitier d'affichage de refroidissement a distance

Also Published As

Publication number Publication date
US20080202140A1 (en) 2008-08-28
CN101142450B (zh) 2011-06-22
HK1118600A1 (en) 2009-02-13
EP1963760A4 (fr) 2011-03-09
JP2008533428A (ja) 2008-08-21
CN101142450A (zh) 2008-03-12
EP1963760A1 (fr) 2008-09-03

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