WO2006101570A1 - Refrigeration transcritique avec vanne de decharge d'addition de pression - Google Patents

Refrigeration transcritique avec vanne de decharge d'addition de pression Download PDF

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Publication number
WO2006101570A1
WO2006101570A1 PCT/US2005/047578 US2005047578W WO2006101570A1 WO 2006101570 A1 WO2006101570 A1 WO 2006101570A1 US 2005047578 W US2005047578 W US 2005047578W WO 2006101570 A1 WO2006101570 A1 WO 2006101570A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
flow path
expansion device
relief valve
pressure
Prior art date
Application number
PCT/US2005/047578
Other languages
English (en)
Inventor
Tobias H. Sienel
Yu Chen
Hans-Joachim Huff
Parmesh Verma
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 JP2008501869A priority Critical patent/JP2008533431A/ja
Priority to US11/908,619 priority patent/US20080184717A1/en
Priority to EP05856051A priority patent/EP1875142A4/fr
Publication of WO2006101570A1 publication Critical patent/WO2006101570A1/fr

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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B2600/2525—Pressure relief 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
    • 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 transcritical refrigeration systems such as CO 2 beverage coolers.
  • Transcritical vapor compression systems have an extra degree of control freedom when compared to subcritical vapor compression systems.
  • pressure in the high and low pressure components of the system are largely controlled by the heat exchanger fluid temperatures.
  • the evaporator pressure is a strong function of the air temperature entering the evaporator
  • the condenser pressure is a strong function of the air temperature entering the condenser. This is because these temperatures are closely correlated with the saturation pressures in the heat exchangers.
  • the high pressure side of the system does not have any saturation properties, and thus pressure is independent from temperature.
  • 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.
  • 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 •omboiV&MaWe oft ⁇ nJnig- ⁇ rt ⁇ ow 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.
  • the controller 50 is coupled to a sensor 52 for measuring the high side pressure.
  • FIG. 1 is a schematic of a prior art CO 2 bottle cooler.
  • FIG. 2 is a schematic of a modified CO 2 bottle cooler.
  • FIG. 3 is a sectional view of a pressure addition relief valve of the cooler of FIG.
  • FIG. 4 is a sectional view of a pressure addition relief valve of the cooler of FIG.
  • FIG. 5 is a graph of discharge pressure against ambient temperature for three different expansion methods.
  • FIG. 6 is a graph of coefficient of performance against ambient temperature for said three different expansion methods.
  • FIG. 7 is a graph of capacity against ambient temperature for said three different expansion methods.
  • FIG. 8 is a graph of discharge pressure against evaporating temperature during pulldown for said three different expansion methods and an inventive method.
  • FIG. 9 is a graph of coefficient of performance against evaporating temperature during pulldown for said three different expansion methods and said inventive method.
  • FIG. 10 is a graph of capacity against evaporating temperature during pulldown for said three different expansion methods and said inventive method.
  • FIG. 11 is a side schematic view of a display case bottle cooler including a refrigeration and air management cassette.
  • FIG. 12 is a view of a refrigeration and air management cassette.
  • a pressure addition relief valve may be used in combination with a primary expansion device.
  • FIG. 2 shows a system 60 formed as a modification of the prior art system 20.
  • the PARV 62 and expansion device 63 are coupled in parallel between a high pressure (upstream) portion 64 of the refrigerant flow path from the gas cooler and a low pressure (downstream) portion 66 to the evaporator.
  • a combination of the pressures at the opposite sides of the PARV 62 acts to open the PARV to permit flow therethrough.
  • the PARV and expansion device may be combined in a combination valve 68.
  • the exemplary valve 68 (FIG.
  • the exemplary body 70 includes a main portion 80 and a cover 82 secured thereto.
  • the exemplary cover seals and secures the periphery of a membrane 84 to the main portion 80.
  • the exemplary membrane is a disk of sheet spring steel. [0027]
  • the membrane has a front face/surface 86 normally engaged/sealed to a seat surface 88 of the body main portion 80.
  • the volumes 76 and 78 have respective ports 90 and 92 in the surface 88.
  • the ports 90 and 92 are normally blocked by engagement with membrane front face 86.
  • the engagement may be assisted by a biasing spring 94 if the particular membrane is not sufficiently self sprung (e.g., a film rather than a metal sheet spring).
  • An exemplary biasing spring 94 is a coil compression spring having a first end 96 engaging the backside/face 98 and a second end 100 engaging an underside 102 of the cover 82.
  • a membrane backside volume (backspace) 104 is formed containing the spring.
  • a port 106 in the cover may expose the backside volume 104 to a reference pressure.
  • the reference pressure may be ambient air pressure, may be a vacuum or other sealed fixed pressure (in which case, the port 106 might be omitted), or a pressure dependent upon a system condition (e.g., connected via a conduit 108 to a TXV-type bulb 110 located elsewhere in the system to provide a variable pressure force). This backside pressure serves to maintain the membrane in its closed condition.
  • the PARV is used in combination with a primary expansion device to provide a better mechanism for controlling the high pressure.
  • the primary expansion device can be a simple orifice as discussed further below, or can be another type of expansion device, such as a capillary tube, TXV, EXV, or other valve.
  • a TXV type valve can be used with the bulb sensing the temperature of the exit of the gas cooler or condenser in one embodiment.
  • a dual bulb TXV can be used to sense the air temperature and gas cooler or condenser discharge difference.
  • an orifice 120 passing a flow 122 provides the principal function of the fixed expansion device portion of the combined valve.
  • PARV may be used to identify both the pure PARV and the combined valve.
  • An exemplary system design may reflect specific design external (ambient) and internal temperatures.
  • An exemplary design ambient temperature is 90 0 F (32°C).
  • An exemplary design pulldown temperature is 16°F (-9 0 C).
  • FIG. 5 shows a plot 400 of discharge pressure against ambient temperature for the optimal control strategy.
  • a plot 402 represents a fixed orifice dimensioned to provide the same pressure at the design ambient pressure. For lower ambient temperatures, the fixed orifice will produce higher than optimum discharge pressure. For higher ambient temperatures, the fixed orifice will produce lower than optimum discharge pressure.
  • a plot 402 represents a fixed orifice dimensioned to provide the same pressure at the design ambient pressure. For lower ambient temperatures, the fixed orifice will produce higher than optimum discharge pressure. For higher ambient temperatures, the fixed orifice will produce lower than optimum discharge pressure.
  • FIG. 6 shows a plot 410 of coefficient of performance against ambient temperature for the optimal control strategy.
  • a plot 412 represents the fixed orifice and a plot 414 represents the constant pressure situation.
  • FIG. 7 shows a plot 420 of capacity against ambient temperature for the optimal control strategy.
  • a plot 422 represents the fixed orifice and a plot 424 represents the constant pressure situation. From FIGS. 5-7 it is seen that that the fixed orifice provides a small difference in pressure relative to the optimal control. This di * flere ⁇ ice ; "causes a relatively modest reduction in efficiency (COP) and an even smaller reduction in capacity. The low cost of the fixed orifice device may outweigh these modest performance reductions. However, there are other considerations. [0036] FIG.
  • FIG 8 shows a plot 430 of discharge pressure against evaporating temperature during pulldown for the optimal control strategy.
  • a plot 432 represents the fixed orifice and a plot 434 represents the constant pressure situation. From the plot 432, it can be seen that pulldown conditions cause the fixed orifice to produce much higher discharge pressures than the optimal control. At higher evaporator temperatures, the resulting high pressures might damage the system. Thus, the problem with using only a simple fixed orifice is that the high (discharge) pressure will exceed a practical design pressure for the system hardware when the low pressure is much higher, such as during a pulldown condition (e.g., when the system is turned on with a high temperature in the volume to be refrigerated and a high ambient temperature).
  • the PARV may function to avoid such high discharge pressures.
  • a plot 436 represents the orifice and PARV combination and is shown departing from the plot 432 at/above a temperature of an exemplary 7.5°C to cap the discharge pressure at an exemplary 1200OkPa selected based upon hardware strength.
  • the PARV will not allow the pressure to exceed a certain value during pulldown, thus preventing damage to the system, and allowing the use of a simple pressure control device such as the fixed orifice device.
  • the effect of the parv strategy on the regulation of the high pressure is a mechanism which acts very close to the optimal pressure control, but which does not over pressurize during periods of excessive refrigerant flow.
  • FIG. 9 shows a plot 440 of coefficient of performance against evaporating temperature during pulldown for the optimal control strategy.
  • a plot 442 represents the fixed orifice
  • a plot 444 represents the constant pressure situation
  • a plot 446 represents the orifice plus PARV combination.
  • FIG. 10 shows a plot 450 of capacity against ambient temperature for the optimal control strategy.
  • a plot 452 represents the fixed orifice
  • a plot 454 represents the constant pressure situation
  • a plot 456 represents the orifice plus PARV combination.
  • Plots 446 and 456 show that efficiency (COP) is not dramatically affected, while capacity is actually gained by the use of the PARV relative to a contolled expansion device regulating to the optimum pressure. The effect of this is that the pulldown time will be reduced and therefore the overall energy consumption of the device will be reduced as well.
  • FIG. 11 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 flow 36 on a recirculating flow path through the interior 206 via the rear duct 210 and top duct 218.
  • FIG. 12 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 28 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)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

Système de réfrigération (20) comprenant une vanne de décharge d'addition de pression (62) en parallèle avec un dispositif d'expansion (63).
PCT/US2005/047578 2005-03-18 2005-12-31 Refrigeration transcritique avec vanne de decharge d'addition de pression WO2006101570A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2008501869A JP2008533431A (ja) 2005-03-18 2005-12-31 増加圧力逃がし弁を備えた遷臨界冷凍
US11/908,619 US20080184717A1 (en) 2005-03-18 2005-12-31 Transcritical Refrigeration With Pressure Addition Relief Valve
EP05856051A EP1875142A4 (fr) 2005-03-18 2005-12-31 Refrigeration transcritique avec vanne de decharge d'addition de pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US66395905P 2005-03-18 2005-03-18
US60/663,959 2005-03-18

Publications (1)

Publication Number Publication Date
WO2006101570A1 true WO2006101570A1 (fr) 2006-09-28

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PCT/US2005/047578 WO2006101570A1 (fr) 2005-03-18 2005-12-31 Refrigeration transcritique avec vanne de decharge d'addition de pression

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US (1) US20080184717A1 (fr)
EP (1) EP1875142A4 (fr)
JP (1) JP2008533431A (fr)
CN (1) CN101142451A (fr)
WO (1) WO2006101570A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010057496A2 (fr) * 2008-11-20 2010-05-27 Danfoss A/S Soupape de détente comprenant un diaphragme et au moins deux ouvertures d’évacuation
DE102019118784A1 (de) * 2019-05-29 2020-12-03 Liebherr-Hausgeräte Ochsenhausen GmbH Kühl- und/oder Gefriergerät

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8047449B2 (en) * 2009-01-28 2011-11-01 Automotive Components Holdings Llc Automotive thermostatic expansion valve with reduced hiss
US9316419B2 (en) 2011-03-31 2016-04-19 Carrier Corporation Expander system
EP2889558B1 (fr) 2013-12-30 2019-05-08 Rolls-Royce Corporation Système de refroidissement avec machine à expansion et éjecteur
CN108831664B (zh) * 2018-05-17 2020-07-17 清华大学 一种用于低温压缩气体腔的具备换能功能的稳压装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5890370A (en) * 1996-01-25 1999-04-06 Denso Corporation Refrigerating system with pressure control valve
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
US6789569B2 (en) * 2000-11-24 2004-09-14 Obrist Engineering Gmbh Pressure relief valve with a spring-loaded membrane closing body

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2618290A (en) * 1949-09-22 1952-11-18 Liquid Carbonic Corp Throttling valve for refrigeration
US4835977A (en) * 1983-11-18 1989-06-06 Teledyne Industries, Inc. Apparatus and method of air-conditioning parked aircraft
DE4432272C2 (de) * 1994-09-09 1997-05-15 Daimler Benz Ag Verfahren zum Betreiben einer Kälteerzeugungsanlage für das Klimatisieren von Fahrzeugen und eine Kälteerzeugungsanlage zur Durchführung desselben
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
DE19852127B4 (de) * 1998-11-12 2008-09-11 Behr Gmbh & Co. Kg Expansionsorgan und hierfür verwendbare Ventileinheit
JP4047497B2 (ja) * 1999-07-08 2008-02-13 株式会社鷺宮製作所 超臨界蒸気圧縮サイクル装置および逃し弁付き圧力制御弁
JP2001116399A (ja) * 1999-10-15 2001-04-27 Zexel Valeo Climate Control Corp 冷凍サイクル
JP2001241807A (ja) * 2000-03-02 2001-09-07 Saginomiya Seisakusho Inc 超臨界蒸気圧縮サイクル装置用逃し弁および複合弁
DE10012714A1 (de) * 2000-03-16 2001-09-20 Egelhof Fa Otto Ventilanordnung einer Kälteanlage
JP2002071037A (ja) * 2000-08-28 2002-03-08 Saginomiya Seisakusho Inc リリーフ弁およびリリーフ弁付き高圧制御弁および超臨界蒸気圧縮冷凍サイクル装置
JP3949417B2 (ja) * 2001-10-10 2007-07-25 株式会社テージーケー 膨張弁
US6550270B2 (en) * 2002-05-24 2003-04-22 The Coca-Cola Company Seal compression mechanism for a refrigeration device
US6626000B1 (en) * 2002-10-30 2003-09-30 Visteon Global Technologies, Inc. Method and system for electronically controlled high side pressure regulation in a vapor compression cycle
US7401472B2 (en) * 2003-01-17 2008-07-22 Tecumseh Products Company Modular heating or cooling system
US20050172654A1 (en) * 2003-11-20 2005-08-11 Hussmann Corporation Modular refrigeration unit
FR2868830B1 (fr) * 2004-04-09 2012-11-30 Valeo Climatisation Dispositif de detente ameliore pour circuit de climatisation
DE102005003967A1 (de) * 2005-01-27 2006-08-03 Otto Egelhof Gmbh & Co. Kg Expansionsventil

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5890370A (en) * 1996-01-25 1999-04-06 Denso Corporation Refrigerating system with pressure control valve
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
US6789569B2 (en) * 2000-11-24 2004-09-14 Obrist Engineering Gmbh Pressure relief valve with a spring-loaded membrane closing body

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010057496A2 (fr) * 2008-11-20 2010-05-27 Danfoss A/S Soupape de détente comprenant un diaphragme et au moins deux ouvertures d’évacuation
WO2010057496A3 (fr) * 2008-11-20 2010-08-19 Danfoss A/S Soupape de détente comprenant un diaphragme et au moins deux ouvertures d’évacuation
CN102292609A (zh) * 2008-11-20 2011-12-21 丹佛斯公司 包括隔膜和至少两个出口孔的膨胀阀
RU2481521C2 (ru) * 2008-11-20 2013-05-10 Данфосс А/С Расширительный клапан, имеющий мембрану и по меньшей мере два выпускных отверстия
DE102019118784A1 (de) * 2019-05-29 2020-12-03 Liebherr-Hausgeräte Ochsenhausen GmbH Kühl- und/oder Gefriergerät

Also Published As

Publication number Publication date
JP2008533431A (ja) 2008-08-21
EP1875142A1 (fr) 2008-01-09
CN101142451A (zh) 2008-03-12
EP1875142A4 (fr) 2008-05-14
US20080184717A1 (en) 2008-08-07

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