EP1855068A2 - Dampfkompressionskühlkreislauf - Google Patents

Dampfkompressionskühlkreislauf Download PDF

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Publication number
EP1855068A2
EP1855068A2 EP07107061A EP07107061A EP1855068A2 EP 1855068 A2 EP1855068 A2 EP 1855068A2 EP 07107061 A EP07107061 A EP 07107061A EP 07107061 A EP07107061 A EP 07107061A EP 1855068 A2 EP1855068 A2 EP 1855068A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
refrigerating cycle
gas
vapor compression
liquid separator
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.)
Withdrawn
Application number
EP07107061A
Other languages
English (en)
French (fr)
Other versions
EP1855068A3 (de
Inventor
Masato Tsuboi
Kenichi Suzuki
Yuuichi Matsumoto
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.)
Sanden Corp
Original Assignee
Sanden 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 Sanden Corp filed Critical Sanden Corp
Publication of EP1855068A2 publication Critical patent/EP1855068A2/de
Publication of EP1855068A3 publication Critical patent/EP1855068A3/de
Withdrawn legal-status Critical Current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
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • 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
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B2600/2501—Bypass valves

Definitions

  • the present invention relates to a vapor compression refrigerating cycle, and specifically, to a vapor compression refrigerating cycle suitable for application to a refrigerating cycle using a natural-system refrigerant which is used also in its critical region.
  • a vapor compression refrigerating cycle obtains its refrigerating ability generally by cooling compressed refrigerant, reducing in pressure the refrigerant by a radiator (a gas cooler) and evaporating the pressure-reduced refrigerant by an evaporator (for example, JP-A-11-193967 ).
  • a conventional refrigerating cycle is formed, for example, as depicted in Fig. 5, and the refrigerating cycle 101 comprises a compressor 102 for compressing refrigerant, a radiator 103 for cooling refrigerant flowed out from compressor 102.
  • an inside heat exchanger 105 for performing heat exchange between high-pressure refrigerant flowed out from radiator 103 and low-pressure refrigerant flowed out from an accumulator 104 (formed also as a gas/liquid separator) and supplying low-pressure refrigerant heat exchanged with high-pressure refrigerant to compressor 102, a pressure reducer 106 for reducing a pressure of high-pressure refrigerant flowed out from inside heat exchanger 105, an evaporator 107 for evaporating low-pressure refrigerant flowed out from pressure reducer 106, and accumulator 104 for storing two-phase refrigerant of liquid-phase refrigerant and gas-phase refrigerant flowed out from evaporator 107 and supplying gas-phase refrigerant to inside heat exchanger 105.
  • a vapor compression refrigerating cycle wherein the refrigerating cycle has an evaporator for evaporating refrigerant, a compressor for compressing refrigerant, a radiator for cooling refrigerant compressed and discharged by the compressor, a first pressure reducer for reducing a pressure of refrigerant cooled by the radiator, and a gas/liquid separator for separating refrigerant flowed out from the first pressure reducer and refrigerant flowed in from the evaporator into gas-phase refrigerant and liquid-phase refrigerant, flowing out the liquid-phase refrigerant to evaporator side and flowing out the gas-phase refrigerant to compressor side, and a pumping means for sending liquid-phase refrigerant flowed out from the gas/liquid separator to evaporator side is provided between the gas/liquid separator and the evaporator ( Japanese Patent Application 2005-358659 , the
  • a vapor compression refrigerating cycle in particular, a vapor compression refrigerating cycle using carbon dioxide refrigerant, which, while exhibiting an advantage according to a basic structure of refrigerating cycle similar to that of the above-described previously proposed vapor compression refrigerating cycle, can reduce the number of parts for forming the refrigerating cycle, thereby reducing the cost of the refrigerating cycle and making the refrigerating cycle small and light in weight as a whole.
  • a vapor compression refrigerating cycle has an evaporator for evaporating refrigerant, a compressor for compressing refrigerant and discharging compressed refrigerant, a radiator for cooling refrigerant compressed and discharged by the compressor, an expander for reducing in pressure and expanding refrigerant cooled by the radiator, and a gas/liquid separator for separating refrigerant flowed out from the expander and refrigerant flowed in from the evaporator into gas-phase refrigerant and liquid-phase refrigerant, flowing out the liquid-phase refrigerant to evaporator side and flowing out the gas-phase refrigerant to compressor side, and is characterized in that a pumping means for sending liquid-phase refrigerant flowed out from the gas/liquid separator to evaporator side is provided between the gas/liquid separator and the evaporator, and at least the pumping means is constructed integrally with the gas/liquid separator.
  • the pumping means may be formed as an axial flow pump.
  • an axial flow pump as shown later in the embodiment, it becomes possible to form the integral structure of the pumping means and the gas/liquid separator as a further compact structure.
  • a structure may be employed wherein a bypass passageway for flowing a part of refrigerant bypassing the expander is provided between the radiator and the gas/liquid separator, and the bypass passageway is also constructed integrally with the gas/liquid separator.
  • a refrigerant pressure before the expander becomes abnormally high it becomes possible to avoid the increase of the refrigerant pressure to an abnormally high pressure by flowing (escaping) the refrigerant to the bypass passageway.
  • bypass passageway integrally with the gas/liquid separator, while realizing a high-efficiency refrigerating cycle, the number of parts (particularly, pipes), the cost, the size and the weight of the refrigerating cycle may be reduced as a whole.
  • a bypass flow rate adjusting means may be provided for adjusting a refrigerant flow rate of the bypass passageway based on a physical amount concerning a condition of the refrigerating cycle.
  • a filter may be provided for preventing passage of foreign matters through a passageway between the radiator and the expander.
  • This filter may be also constructed integrally with the gas/liquid separator.
  • a structure may be employed wherein a heat exchanger is provided for heat exchange between high-pressure refrigerant flowed out from the radiator and low-pressure refrigerant flowed into the compressor, similarly to an inside heat exchanger in the conventional technology.
  • the thermal energy in the refrigerating cycle may be utilized more efficiently.
  • Such a vapor compression refrigerating cycle according to the present invention is suitable for application to a refrigerating cycle having a supercritical region, in particular, to a refrigerating cycle using carbon dioxide as refrigerant. Further, the vapor compression refrigerating cycle according to the present invention is suitable as a refrigerating cycle used for an air conditioning system for a vehicle.
  • the pumping means preferably together with other equipment and other parts
  • the gas/liquid separator namely, by forming an integrated module including the gas/liquid separator and at least the pumping means, it becomes possible to decrease the number of parts of the refrigerating cycle using refrigerant which is operated in a supercritical region. Via this integrated module, the cost, the size and the weight of the refrigerating cycle may be reduced as a whole.
  • Fig. 1 depicts a vapor compression refrigerating cycle according to a first embodiment of the present invention, using carbon dioxide which is a natural-system refrigerant.
  • Refrigerating cycle 1 depicted in Fig. 1 comprises a compressor 2 for compressing refrigerant and discharging the compressed refrigerant, a radiator 3 for cooling refrigerant compressed and discharged by compressor 2.
  • an expander 4 for reducing in pressure and expanding refrigerant cooled by radiator 3, a gas/liquid separator 5 for separating refrigerant flowed out from expander 4 and refrigerant flowed in from an evaporator 6 into gas-phase refrigerant and liquid-phase refrigerant, flowing out the liquid-phase refrigerant to the evaporator side and flowing out the gas-phase refrigerant to the compressor side, and evaporator 6 for evaporating liquid-phase refrigerant flowed out from gas/liquid separator 5 to gas-phase refrigerant.
  • Refrigerating cycle I has a pumping means 7 provided between gas/liquid separator 5 and evaporator 6 for sending liquid-phase refrigerant flowed out from the gas/liquid separator 5 to the evaporator side, and at least the pumping means 7 is constructed integrally with the gas/liquid separator 5.
  • expander 4 is also constructed integrally with gas/liquid separator 5 (it is incorporated into a gas/liquid separator integrated module 8), and the expander 4 and pumping means 7 are connected coaxially to each other by an identical shaft 9 to utilize the expansion energy of refrigerant recovered in the expander 4 as an energy for driving the pumping means 7.
  • a bypass passageway 10 for flowing a part of refrigerant bypassing expander 4 is provided between radiator 3 and gas/liquid separator 5.
  • This bypass passageway 10 is also constructed integrally with gas/liquid separator 5 and it is incorporated into gas/liquid separator integrated module 8.
  • a bypass valve 1 I is provided as a bypass flow rate adjusting means for adjusting a refrigerant flow rate of bypass passageway 10 based on a physical amount concerning a condition of refrigerating cycle 1.
  • a pressure reducer 12 may be provided between pumping menas 7 and evaporator 6 for adjusting refrigerant being flowed into evaporator 6 to a lower-pressure refrigerant more suitable for being evaporated.
  • This pressure reducer 12 may be structured as one having a mechanism in which a degree of pressure reduction is determined based on information concerning a condition of refrigerating cycle 1. In this case, this mechanism may be either an autonomous mechanism operating based on a pressure difference of refrigerant between pressures before and after the mechanism, or a mechanism operated by an external electric signal or a pressure signal.
  • An introduction port 22 for introducing refrigerant 21 from radiator 3 and a discharge port 24 for sending at a pressurized condition and flowing out refrigerant 23 to the side of evaporator 6 are provided to gas/liquid separator integrated module 8.
  • a flowing-in port 26 for flowing in refrigerant 25 from evaporator 6 and a discharge port 28 for flowing out gas-phase refrigerant 27 separated by gas/liquid separator 5 to the side of compressor 2 are provided to gas/liquid separator 5.
  • a filter 29 is provided at a position downstream of introduction port 22 in gas/liquid separator integrated module 8 for preventing passage of foreign matters through a refrigerant passageway between radiator 3 and expander 4, and the filter 29 is also incorporated into gas/liquid separator integrated module 8.
  • bypass passageway 10 is formed by being diverged from the refrigerant passageway reaching expander 4, and in this bypass passageway 10, the aforementioned bypass valve 11 is provided.
  • This bypass valve 11 is formed as a refrigerant flow rate adjusting type bypass valve for changing a refrigerant flow rate in accordance with a pressure difference between before and after it.
  • bypass valve 11 When the pressure of high-pressure refrigerant exceeds its threshold value, bypass valve 11 communicates by short cut between the high-pressure side refrigerant passageway at the upstream side of bypass valve 11 and the low -pressure side refrigerant passageway formed in the inside of gas/liquid separator 5, or bypass valve 11 adjusts the pressure of the low -pressure side refrigerant passageway.
  • the refrigerant which is not bypassed by bypass passageway 10, is sent to expander 4, and the refrigerant expanded by expander 4 is joined to the refrigerant sent from bypass passageway 10, and thereafter, introduced into gas/liquid separator 5 through inlet port 30 of gas/liquid separator 5.
  • introduced refrigerant 31 is joined to refrigerant 25 introduced from evaporator 6, and the joined refrigerant is separated in gas/liquid separator 5 into gas-phase refrigerant 32 and liquid-phase refrigerant 33.
  • the separated gas-phase refrigerant 32 is sent from discharge port 28 to the side of compressor 2 through a U-shaped inside pipe 34, and the separated liquid-phase refrigerant 33 is sent from discharge port 35 to pumping means 7.
  • pumping means 7 is formed as an axial flow pump, and as aforementioned, it is connected to expander 4 by identical shaft 9.
  • This connection shaft 9 is supported, for example, by a bearing 43, and further, it may be supported by a guide impeller of the axial flow pump provided as pumping means 7.
  • This portion incorporated with pumping means 7 and the inside of gas/liquid separator 5 communicating with this portion are formed as a low-pressure chamber at a pressure lower than a supercritical pressure.
  • refrigerating machine oil 37 which has been contained in refrigerant, is stored in the bottom portion in gas/liquid separator 5 at a position lower than separated liquid-phase refrigerant 33, this refrigerating machine oil 37 is returned to the side of compressor 2 through an oil return hole 38 provided on the bottom part of inside pipe 34, and served for lubrication.
  • refrigerating cycle 1 thus constructed, by the structure in which gas/liquid separator 5 and at least pumping means 7 are integrated as gas/liquid separator integrated module 8, at least pipes at this portion, which have been needed in the conventional technology, can be omitted, and it becomes possible to decrease the number of parts and to reduce the cost, the size and the weight of refrigerating cycle 1 as a whole. Further, as in the above-described embodiment, by incorporating other parts (at least any of filter 29, bypass passageway 10 and expander 4) integrally into gas/liquid separator integrated module 8, it becomes possible to further decrease the number of parts and to further the cost, the size and the weight of refrigerating cycle 1.
  • Fig. 4 depicts a vapor compression refrigerating cycle 41 according to a second embodiment of the present invention.
  • a refrigerant heat exchanger 42 for exchanging in heat between the high-pressure refrigerant flowed out from radiator 3 and the low-pressure refrigerant flowed into compressor 2 is provided to the refrigerating cycle having a structure similar to that of the first embodiment.
  • the thermal energy in refrigerating cycle 41 is utilized more effectively, and it becomes possible to realize a refrigerating cycle having a better efficiency in consumption power or energy.
  • the advantage according to the integration structure due to gas/liquid separator integrated module 8 similar to that in the first embodiment may be obtained also in this embodiment.
  • the vapor compression refrigerating cycle according to the present invention is suitable, in particular, for a refrigerating cycle using carbon dioxide which is a natural-system refrigerant, and especially, suitable as a refrigerating cycle used for an air conditioning system for vehicles.

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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)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
EP07107061A 2006-05-10 2007-04-26 Dampfkompressionskühlkreislauf Withdrawn EP1855068A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006131131A JP2007303709A (ja) 2006-05-10 2006-05-10 冷凍サイクル

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EP1855068A2 true EP1855068A2 (de) 2007-11-14
EP1855068A3 EP1855068A3 (de) 2008-11-05

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009061268A1 (en) * 2007-11-05 2009-05-14 Alfa Laval Corporate Ab Liquid separator for an evaporator system
CN101765749A (zh) * 2008-06-03 2010-06-30 松下电器产业株式会社 制冷循环装置
WO2013117187A3 (de) * 2012-02-09 2013-11-21 Viessmann Werke Gmbh & Co. Kg Wärmepumpenvorrichtung
EP3159626A1 (de) * 2015-10-20 2017-04-26 Ulrich Brunner GmbH Wärmepumpenkreislauf
EP3159627A1 (de) * 2015-10-20 2017-04-26 Ulrich Brunner GmbH Kältemediumkreislauf
DE102016101292A1 (de) * 2016-01-26 2017-07-27 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kühlvorrichtung für eine elektrische Antriebseinheit eines Fahrzeugs
DE102021131788A1 (de) 2021-12-02 2023-06-07 Valeo Klimasysteme Gmbh Kältemittelkreislauf und Kühlsystem für Fahrzeuge

Citations (8)

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Publication number Priority date Publication date Assignee Title
EP0260367A1 (de) * 1986-09-16 1988-03-23 Smentek, Annemarie Kälteanlage
EP1043550A1 (de) * 1997-12-26 2000-10-11 Zexel Corporation Kältekreislauf
EP1046869A1 (de) * 1999-04-20 2000-10-25 Sanden Corporation Kühl- und Klimatisierungssystem
DE10001470A1 (de) * 2000-01-15 2001-07-19 Max Karsch Verfahren zum Betreiben einer Klimatisierungseinrichtung für Fahrzeuge und Ausführung des erforderlichen Abscheidesammlers
WO2003056256A1 (en) * 2001-12-21 2003-07-10 Phil-Chan Rha Refrigerator having a expansion unit to execute condensing function
JP2004108220A (ja) * 2002-09-18 2004-04-08 Mitsubishi Heavy Ind Ltd ボトミングサイクル発電システム
DE10358428A1 (de) * 2003-12-13 2005-07-07 Grasso Gmbh Refrigeration Technology Kälteanlage für transkritische Betriebsweise mit Economiser
JP2005300031A (ja) * 2004-04-13 2005-10-27 Matsushita Electric Ind Co Ltd 冷凍サイクル装置およびその制御方法

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JPS62252870A (ja) * 1986-04-23 1987-11-04 株式会社　前川製作所 冷凍又はヒ−トポンプサイクルにおける冷媒流量制御方法
JP3811116B2 (ja) * 2001-10-19 2006-08-16 松下電器産業株式会社 冷凍サイクル装置
JP3708536B1 (ja) * 2004-03-31 2005-10-19 松下電器産業株式会社 冷凍サイクル装置およびその制御方法
JP2006064257A (ja) * 2004-08-26 2006-03-09 Daikin Ind Ltd 空調室内機および冷凍装置

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EP0260367A1 (de) * 1986-09-16 1988-03-23 Smentek, Annemarie Kälteanlage
EP1043550A1 (de) * 1997-12-26 2000-10-11 Zexel Corporation Kältekreislauf
EP1046869A1 (de) * 1999-04-20 2000-10-25 Sanden Corporation Kühl- und Klimatisierungssystem
DE10001470A1 (de) * 2000-01-15 2001-07-19 Max Karsch Verfahren zum Betreiben einer Klimatisierungseinrichtung für Fahrzeuge und Ausführung des erforderlichen Abscheidesammlers
WO2003056256A1 (en) * 2001-12-21 2003-07-10 Phil-Chan Rha Refrigerator having a expansion unit to execute condensing function
JP2004108220A (ja) * 2002-09-18 2004-04-08 Mitsubishi Heavy Ind Ltd ボトミングサイクル発電システム
DE10358428A1 (de) * 2003-12-13 2005-07-07 Grasso Gmbh Refrigeration Technology Kälteanlage für transkritische Betriebsweise mit Economiser
JP2005300031A (ja) * 2004-04-13 2005-10-27 Matsushita Electric Ind Co Ltd 冷凍サイクル装置およびその制御方法

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Title
SCHIESARO P ET AL: "DEVELOPMENT OF A TWO STAGE CO2 SUPERMARKET SYSTEM" IIR CONFERENCE. NEW TECHNOLOGIES IN COMMERCIAL REFRIGERATION, XX, XX, 22 July 2002 (2002-07-22), pages 1-10, XP001169091 *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009061268A1 (en) * 2007-11-05 2009-05-14 Alfa Laval Corporate Ab Liquid separator for an evaporator system
US10036583B2 (en) 2007-11-05 2018-07-31 Alfa Laval Corporated Ab Liquid separator for an evaporator system
CN101765749A (zh) * 2008-06-03 2010-06-30 松下电器产业株式会社 制冷循环装置
WO2013117187A3 (de) * 2012-02-09 2013-11-21 Viessmann Werke Gmbh & Co. Kg Wärmepumpenvorrichtung
EP3159626A1 (de) * 2015-10-20 2017-04-26 Ulrich Brunner GmbH Wärmepumpenkreislauf
EP3159627A1 (de) * 2015-10-20 2017-04-26 Ulrich Brunner GmbH Kältemediumkreislauf
DE102016101292A1 (de) * 2016-01-26 2017-07-27 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kühlvorrichtung für eine elektrische Antriebseinheit eines Fahrzeugs
DE102021131788A1 (de) 2021-12-02 2023-06-07 Valeo Klimasysteme Gmbh Kältemittelkreislauf und Kühlsystem für Fahrzeuge

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EP1855068A3 (de) 2008-11-05
JP2007303709A (ja) 2007-11-22

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