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EP2187150A2 - Cycle de réfrigération - Google Patents

Cycle de réfrigération Download PDF

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Publication number
EP2187150A2
EP2187150A2 EP09175357A EP09175357A EP2187150A2 EP 2187150 A2 EP2187150 A2 EP 2187150A2 EP 09175357 A EP09175357 A EP 09175357A EP 09175357 A EP09175357 A EP 09175357A EP 2187150 A2 EP2187150 A2 EP 2187150A2
Authority
EP
European Patent Office
Prior art keywords
temperature
expansion valve
refrigerant
refrigerating cycle
compressor
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Withdrawn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
EP09175357A
Other languages
German (de)
English (en)
Other versions
EP2187150A3 (fr
Inventor
Tomonori Shimura
Eiji Fukuda
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.)
Fujikoki Corp
Original Assignee
Fujikoki 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 Fujikoki Corp filed Critical Fujikoki Corp
Publication of EP2187150A2 publication Critical patent/EP2187150A2/fr
Publication of EP2187150A3 publication Critical patent/EP2187150A3/fr
Withdrawn legal-status Critical Current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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/068—Expansion valves combined with a sensor
    • F25B2341/0683—Expansion valves combined with a sensor the sensor is disposed in the suction line and influenced by the temperature or the pressure of the suction gas
    • 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor

Definitions

  • the present invention relates to a refrigerating cycle used for a car air-conditioner and the like, and particularly relates to a refrigerating cycle including a compressor, a condenser, an evaporator, an internal heat exchanger, and an expansion valve, wherein a heat exchange is carried out between a high-temperature refrigerant introduced from the condenser to the expansion valve and a low-temperature refrigerant introduced from the evaporator to the suction side of the compressor in the internal heat exchanger.
  • a refrigerating cycle illustrated in Fig. 9 has been proposed and practically used in order to improve refrigerating capacity, etc. That is, a refrigerating cycle 10 illustrated in Fig. 9 includes a compressor 101, a condenser 102, an evaporator 103, an internal heat exchanger 104, and an expansion valve 110 (which will be described below).
  • a heat exchange is carried out between a high-temperature and high-pressure refrigerant (liquid phase) introduced from the condenser 102 to the expansion valve 110 and a low-temperature and low-pressure refrigerant (vapor phase) introduced from the evaporator 103 to the suction side of the compressor 101 in the internal heat exchanger 104.
  • a high-temperature and high-pressure refrigerant liquid phase
  • a low-temperature and low-pressure refrigerant vapor phase
  • the expansion valve 110 illustrated in Fig. 10 includes an inflow orifice 21 and a valve chamber 24 at a lower part of a valve main body 20.
  • the inflow orifice 21 is for introducing a high-temperature refrigerant from the internal heat exchanger 104, and the valve chamber 24 has a valve seat part 25 (a valve port 26).
  • the expansion valve 110 further includes an outflow orifice 22 at a center part of the valve main body 20.
  • the expansion valve 110 further includes a temperature-sensitive inflow orifice 31 and an outflow orifice 32 at the left and right of an upper part of the valve main body 20.
  • the expansion valve 110 further includes a diaphragm device 40 as a temperature-sensitive and pressure-sensitive responding means at the uppermost part of the valve main body 20, and the diaphragm device 40 responds to a temperature change and a pressure change of a refrigerant flowing from the temperature-sensitive inflow orifice 31 to the outflow orifice 32.
  • a diaphragm device 40 as a temperature-sensitive and pressure-sensitive responding means at the uppermost part of the valve main body 20, and the diaphragm device 40 responds to a temperature change and a pressure change of a refrigerant flowing from the temperature-sensitive inflow orifice 31 to the outflow orifice 32.
  • a ball valve body 30 for opening and closing the valve port 26 and a coil spring 27 for urging the ball valve body 30 toward the valve closing direction are arranged.
  • the diaphragm device 40 has a diaphragm 42 for driving the ball valve body 30 in the opening and closing direction (the vertical direction) through a drive rod 35 and a connector 36.
  • An upper pressure chamber 43 and a lower pressure chamber 44 are partitioned at the upper and lower sides of the diaphragm 42 used as a partition wall.
  • the upper pressure chamber 43 encloses gas at a predetermined pressure, and is sealed by a cap 46.
  • the lower pressure chamber 44 communicates with the temperature-sensitive inflow orifice 31 and the outflow orifice 32 through a communication opening 45, and pressure of the low-temperature refrigerant introduced from the evaporator 103 to the internal heat exchanger 104 acts on the lower face side of the diaphragm 42.
  • a hole 38 is formed near an internal center part of the valve main body 20 where the drive rod 35 penetrates, and an O-ring 39 as a sealing member is interposed between an inner peripheral face of the hole 38 and an outer peripheral face of the drive rod 35.
  • a spring pressure-adjusting nut 28 is screwed to a lower part of the valve chamber 24, and an O-ring 29 as a sealing member is interposed between a not-screwed part of the spring pressure-adjusting nut 28 and an inner peripheral face of the valve chamber 24.
  • a flow rate (a pressure drop rate and a temperature drop rate) of the refrigerant introduced from the outflow orifice 22 to the evaporator 103 is adjusted responding to a temperature and pressure of the low-temperature refrigerant before carrying out a heat exchange in the internal heat exchanger 104.
  • Japanese Patent Application Laid-Open No. 2000-346466 discusses a method of detecting refrigerant temperature at a suction side of a compressor and adjusting the amount of a refrigerant flowing in an internal heat exchanger by a three-way valve.
  • this method needs the three-way valve, a piping system becomes to be complicated and the number of parts tends to increase.
  • Japanese Patent Application Laid-Open No. 2007-240041 discusses a method of providing a bypass passage at an expansion valve and cooling a refrigerant.
  • this method when a load to the system fluctuates, refrigerant temperature at the compressor suction side cannot be controlled, and a structure of the expansion valve becomes to be complicated to increase cost.
  • the present invention is to solve the aforementioned problems, and is directed to provide a refrigerating cycle capable of certainly and effectively suppressing an excessive increase of refrigerant temperature at the suction side of the compressor without complicating a piping system and a structure of an expansion valve.
  • a refrigerating cycle of the present invention basically includes a compressor, a condenser, an evaporator, an internal heat exchanger, and an expansion valve.
  • a heat exchange is carried out between a high-temperature refrigerant introduced from the condenser to the expansion valve and a low-temperature refrigerant introduced from the evaporator to the suction side of the compressor.
  • a temperature-sensitive cylinder and/or an external pressure introduction pipe are additionally provided at the expansion valve.
  • a flowing rate of a refrigerant introduced to the evaporator is adjusted responding to temperature and/or pressure of a low-temperature refrigerant after the heat exchange.
  • the expansion valve includes a drive means such as a diaphragm device which drives a valve body in opening and closing directions responding to a pressure change of a low-temperature refrigerant introduced through the external pressure introduction pipe after carrying out the heat exchange.
  • a drive means such as a diaphragm device which drives a valve body in opening and closing directions responding to a pressure change of a low-temperature refrigerant introduced through the external pressure introduction pipe after carrying out the heat exchange.
  • the expansion valve includes a drive means such as a diaphragm device which drives a valve body in the opening and closing directions responding to a temperature change of a low-temperature refrigerant detected by the temperature-sensitive cylinder after carrying out the heat exchange.
  • a drive means such as a diaphragm device which drives a valve body in the opening and closing directions responding to a temperature change of a low-temperature refrigerant detected by the temperature-sensitive cylinder after carrying out the heat exchange.
  • the refrigerating cycle includes the temperature-sensitive cylinder and/or the external refrigerant pressure introduction pipe for detecting the temperature and/or pressure of the low-temperature refrigerant introduced toward the suction side of the compressor after carrying out the heat exchange in the internal heat exchanger.
  • a flowing rate (a pressure drop rate and a temperature drop rate) of the refrigerant introduced to the evaporator is adjusted responding to temperature and/or pressure of the low-temperature refrigerant after the heat exchange.
  • the refrigerating cycle of the present invention can acquire the aforementioned effect only by slightly remodeling a currently used refrigerating cycle and an expansion valve used in it, so that there is a merit that the present invention does not greatly increase cost.
  • Figs. 1(A), 1(B), and 1(C) illustrate a first exemplary embodiment, a second exemplary embodiment, and a third exemplary embodiment respectively of a refrigerating cycle according to the present invention.
  • Figs. 2 , 3 and 4 illustrate expansion valves 111, 112 and 113 used in the first, second and third exemplary embodiments respectively.
  • refrigerating cycles 11, 12, and 13 illustrated in Figs. 1(A), 1(B), and 1(C) and as for the expansion valves 111, 112, and 113 illustrated in Figs. 2 to 4 , same reference numerals are given to parts corresponding to respective parts of the conventional example of the refrigerating cycle 10 and the expansion valve 110 used therein, which are illustrated in Figs. 9 and 10 , and differences from the conventional example will be mainly described below.
  • an external pressure introduction pipe 50 is connected to an intermediate part of a pipe 125 connecting the internal heat exchanger 104 and the suction side of the compressor 101.
  • Another end of the external pressure introduction pipe 50 is connected with a pressure introducing passage 54 provided near a bottom part of a lower pressure chamber 44 of the expansion valve 111.
  • a flowing rate (a pressure drop rate and a temperature drop rate) of the refrigerant introduced to an evaporator 103 is adjusted responding to pressure of the low-temperature refrigerant after the heat exchange.
  • a communication opening 45 of the conventional example is changed to a rod insertion hole 62 having a small diameter.
  • An O-ring 63 as a sealing member is interposed between the rod insertion hole 62 and a drive rod 35, and the pressure of the low-temperature refrigerant after carrying out the heat exchange in the internal heat exchanger 104 is introduced into the lower pressure chamber 44 through the external pressure introduction pipe 50 and the pressure introduction passage 54.
  • the refrigerating cycle 11 of this exemplary embodiment includes the external refrigerant pressure introduction pipe 50 for detecting pressure of the low-temperature refrigerant introduced toward the suction side of the compressor 101 after carrying out the heat exchange in the internal heat exchanger 104.
  • the expansion valve 111 the flowing rate of the refrigerant introduced to the evaporator 103 is adjusted responding to the pressure of the low-temperature refrigerant after the heat exchange.
  • the refrigerating cycle of this exemplary embodiment can acquire the aforementioned effect only by slightly remodeling a currently used refrigerating cycle and an expansion valve used in the refrigerating cycle, so that there is a merit that the present invention does not greatly increase cost.
  • a temperature-sensitive cylinder 70 is arranged closely to a pipe 125 connecting the internal heat exchanger 104 and the suction side of the compressor 101. Further, as illustrated in Fig. 3 , the temperature-sensitive cylinder 70 and an upper pressure chamber 43 of the expansion valve 112 are connected with a capillary tube 72, and a flowing rate of the refrigerant introduced to an evaporator 103 is adjusted responding to temperature of the low-temperature refrigerant after the heat exchange in the expansion valve 112.
  • the refrigerating cycle 12 having this configuration includes the temperature-sensitive cylinder 70 to detect the temperature of the low-temperature refrigerant introduced to the suction side of the compressor 101 after carrying out the heat exchange in the internal heat exchanger 104, and the flowing rate of the refrigerant introduced to the evaporator 103 is adjusted responding to the temperature of the low-temperature refrigerant after the heat exchange in the expansion valve 112.
  • an excessive increase of the refrigerant temperature at the suction side of the compressor 101 can be certainly and effectively suppressed without complicating a piping system and a structure of the expansion valve, like the first exemplary embodiment. Therefore, since an excessive increase of (discharge) temperature in the compressor can be previously prevented, oil contained in the refrigerant can be prevented from degradation, and thus faults such as burn-out can be prevented.
  • the refrigerating cycle of this exemplary embodiment can acquire the aforementioned effect only by slightly remodeling a currently used refrigerating cycle and an expansion valve used in the refrigerating cycle, so that there also is a merit that the present invention does not greatly increase cost.
  • the refrigerating cycle 13 of the third exemplary embodiment is a combination of the refrigerating cycle 11 of the first exemplary embodiment and the refrigerating cycle 12 of the second exemplary embodiment.
  • the refrigerating cycle 13 includes both the external pressure introduction pipe 50 and the temperature-sensitive cylinder 70.
  • a configuration around the lower pressure chamber 44 of an expansion valve 113 used therefore is approximately similar to the configuration of the first exemplary embodiment, and a configuration around the upper pressure chamber 43 is approximately similar to the configuration of the second exemplary embodiment.
  • a flowing rate of the refrigerant introduced to an evaporator 103 is adjusted responding to temperature and pressure of the low-temperature refrigerant after the heat exchange.
  • Figs. 5(A), 5(B) and 5(C) illustrate a fourth exemplary embodiment, a fifth exemplary embodiment, and a sixth exemplary embodiment of a refrigerating cycle according to the present invention.
  • Fig. 6 illustrates an expansion valve 114 used in the fourth exemplary embodiment.
  • Fig. 7 illustrates an expansion valve 115 used in the fifth exemplary embodiment.
  • Fig. 8 illustrates an expansion valve 116 used in the sixth exemplary embodiment.
  • the refrigerating cycles 14 15 and 16 illustrated in Figs. 5(A), 5(B), and 5(C)
  • the expansion valves 114, 115, and 116 used in the refrigerating cycles 14, 15, and 16 of the fourth, fifth, and sixth exemplary embodiments do not include the temperature-sensitive inflow orifice 31 and the outflow orifice 32, which are provided in the expansion valves 111, 112, and 113 used in the refrigerating cycles 11, 12, and 13 of the first, second, and third exemplary embodiments.
  • a low-temperature refrigerant introduced from an evaporator 103 does not pass the insides of the expansion valves 114, 115 and 116, but is directly introduced to an internal heat exchanger 104.
  • the refrigerating cycle 14 of the fourth exemplary embodiment is similar to the refrigerating cycle 12 of the second exemplary embodiment regarding described below.
  • a temperature-sensitive cylinder 70 is arranged closely to a pipe 125 connecting the internal heat exchanger 104 and the suction side of the compressor 101. Further, as illustrated in Fig.
  • a valve main body 20 of the expansion valve 114 used in this exemplary embodiment includes an internal pressure passage 66 for communicating between the lower pressure chamber 44 and the outflow orifice 22.
  • a temperature-sensitive cylinder usually detects the refrigerant temperature near the outflow orifice of the evaporator 103 (refer to Fig. 5(B) ).
  • the temperature-sensitive cylinder 70 detects the refrigerant temperature after carrying out the heat exchange in the internal heat exchanger 104. That is, it is characterized that a position of the temperature-sensitive cylinder 70 is changed.
  • the refrigerating cycle 14 having the aforementioned configuration can acquire effects which are approximately similar to the effects of the refrigerating cycle 12 of the second exemplary embodiment.
  • the refrigerating cycle 15 of the fifth exemplary embodiment is similar to the refrigerating cycle 11 of the first exemplary embodiment regarding described below.
  • the refrigerating cycle 15 in order to detect pressure of a low-temperature refrigerant introduced to the suction side of a compressor 101 after carrying out a heat exchange in an internal heat exchanger 104, one end of the external pressure introduction pipe 50 is connected with the intermediate part of the pipe 125 connecting the internal heat exchanger 104 and the suction side of the compressor 101.
  • Another end of the external pressure introduction pipe 50 is connected with a L-shaped pressure introducing passage 54 for communicating between a lower pressure chamber 44 of the expansion valve 115 and the external.
  • a flowing rate of a refrigerant introduced to an evaporator 103 is adjusted responding to pressure of the low-temperature refrigerant after the heat exchange.
  • the temperature-sensitive cylinder 70 is arranged closely to a pipe 124 (near an outflow orifice of the evaporator 103) for connecting the evaporator 103 and the internal heat exchanger 104, and the temperature-sensitive cylinder 70 and an upper pressure chamber 43 of the expansion valve 115 are connected with a capillary tube 72.
  • the refrigerating cycle 15 having the aforementioned configuration can acquire effects which are approximately similar to the effects of the refrigerating cycle 11 of the first exemplary embodiment.
  • the refrigerating cycle 16 of the sixth exemplary embodiment is a combination of the refrigerating cycle 14 of the fourth exemplary embodiment and the refrigerating cycle 15 of the fifth exemplary embodiment.
  • the refrigerating cycle 16 includes both the external pressure introduction pipe 50 and the temperature-sensitive cylinder 70.
  • a configuration around the lower pressure chamber 44 of the expansion valve 116 used in the refrigerating cycle 16 is approximately similar to the configuration of the fifth exemplary embodiment, and a configuration around the upper pressure chamber 43 is approximately similar to the configuration of the fourth exemplary embodiment.
  • a flowing rate of a refrigerant introduced to an evaporator 103 is adjusted responding to the pressure and temperature of the low-temperature refrigerant after the heat exchange.

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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)
  • Temperature-Responsive Valves (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP09175357.4A 2008-11-18 2009-11-09 Cycle de réfrigération Withdrawn EP2187150A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2008294844A JP2010121831A (ja) 2008-11-18 2008-11-18 冷凍サイクル

Publications (2)

Publication Number Publication Date
EP2187150A2 true EP2187150A2 (fr) 2010-05-19
EP2187150A3 EP2187150A3 (fr) 2014-01-15

Family

ID=41818427

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09175357.4A Withdrawn EP2187150A3 (fr) 2008-11-18 2009-11-09 Cycle de réfrigération

Country Status (3)

Country Link
EP (1) EP2187150A3 (fr)
JP (1) JP2010121831A (fr)
CN (1) CN101737987A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103017409A (zh) * 2013-01-15 2013-04-03 吴秀华 节能高效制冷、制热一体机
US8931305B2 (en) 2010-03-31 2015-01-13 Denso International America, Inc. Evaporator unit
FR3028016A1 (fr) * 2014-10-30 2016-05-06 Valeo Systemes Thermiques Dispositif de gestion thermique de vehicule automobile
FR3028015A1 (fr) * 2014-10-30 2016-05-06 Valeo Systemes Thermiques Dispositif de gestion thermique de vehicule automobile

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102530803B (zh) * 2012-01-12 2013-06-05 苏权兴 制冷剂分装设备
EP2977244B1 (fr) * 2014-07-24 2016-06-29 C.R.F. Società Consortile per Azioni Climatisation pour véhicules
CN113654284B (zh) * 2020-05-12 2024-06-25 浙江三花商用制冷有限公司 感温部件及具有该感温部件的制冷系统
CN120274437B (zh) * 2025-04-08 2025-11-18 东莞信易电热机械有限公司 一种具有智能调节功能的冷水机

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000346466A (ja) 1999-06-02 2000-12-15 Sanden Corp 蒸気圧縮式冷凍サイクル
JP2007240041A (ja) 2006-03-07 2007-09-20 Tgk Co Ltd 膨張弁

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JP2902853B2 (ja) * 1992-04-27 1999-06-07 三洋電機株式会社 空気調和機
JPH0648275Y2 (ja) * 1988-06-13 1994-12-12 三菱重工業株式会社 ヒートポンプ
JPH06241580A (ja) * 1993-02-18 1994-08-30 Nippondenso Co Ltd 冷凍サイクル装置
BR9713110A (pt) * 1996-11-19 2000-04-11 Danfoss As Processo para o controle de um sistema de refrigeração, bem como um sistema de refrigeração e válvula de expansão.
JP4323619B2 (ja) * 1999-06-17 2009-09-02 株式会社日本クライメイトシステムズ 車両用空調装置
US6460358B1 (en) * 2000-11-13 2002-10-08 Thomas H. Hebert Flash gas and superheat eliminator for evaporators and method therefor
JP4246189B2 (ja) * 2005-09-07 2009-04-02 株式会社デンソー 冷凍サイクル装置
JP2008122034A (ja) * 2006-11-15 2008-05-29 Sanden Corp 車両用冷房装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000346466A (ja) 1999-06-02 2000-12-15 Sanden Corp 蒸気圧縮式冷凍サイクル
JP2007240041A (ja) 2006-03-07 2007-09-20 Tgk Co Ltd 膨張弁

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8931305B2 (en) 2010-03-31 2015-01-13 Denso International America, Inc. Evaporator unit
CN103017409A (zh) * 2013-01-15 2013-04-03 吴秀华 节能高效制冷、制热一体机
CN103017409B (zh) * 2013-01-15 2015-12-02 吴秀华 节能高效制冷、制热一体机
FR3028016A1 (fr) * 2014-10-30 2016-05-06 Valeo Systemes Thermiques Dispositif de gestion thermique de vehicule automobile
FR3028015A1 (fr) * 2014-10-30 2016-05-06 Valeo Systemes Thermiques Dispositif de gestion thermique de vehicule automobile

Also Published As

Publication number Publication date
EP2187150A3 (fr) 2014-01-15
JP2010121831A (ja) 2010-06-03
CN101737987A (zh) 2010-06-16

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