EP1832822A2 - Expansionsventil - Google Patents

Expansionsventil Download PDF

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Publication number
EP1832822A2
EP1832822A2 EP07003767A EP07003767A EP1832822A2 EP 1832822 A2 EP1832822 A2 EP 1832822A2 EP 07003767 A EP07003767 A EP 07003767A EP 07003767 A EP07003767 A EP 07003767A EP 1832822 A2 EP1832822 A2 EP 1832822A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
expansion valve
pressure
hole
passage
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.)
Granted
Application number
EP07003767A
Other languages
English (en)
French (fr)
Other versions
EP1832822B1 (de
EP1832822A3 (de
Inventor
Hisatoshi Hirota
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.)
TGK Co Ltd
Original Assignee
TGK Co Ltd
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 TGK Co Ltd filed Critical TGK Co Ltd
Publication of EP1832822A2 publication Critical patent/EP1832822A2/de
Publication of EP1832822A3 publication Critical patent/EP1832822A3/de
Application granted granted Critical
Publication of EP1832822B1 publication Critical patent/EP1832822B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F25B41/32—Expansion valves having flow rate limiting means other than the valve member, e.g. having bypass orifices in the valve body
    • 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for evaporators
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for expansion valves or capillary tubes
    • 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
    • F25B2500/06—Damage
    • 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
    • F25B2500/08—Exceeding a certain temperature value in a refrigeration component or cycle

Definitions

  • the invention relates to an expansion valve according to the preamble of claim 1, for a refrigeration cycle of an automotive air conditioner.
  • carbon dioxide may be used as the refrigerant in place of a CFC substitute (HFC-134a in refrigeration cycles for automotive air conditioners.
  • an internal heat exchanger is generally used in such refrigeration cycles ( JP-A-2001-108308 ).
  • the internal heat exchanger exchanges heat between refrigerant flowing from a gas cooler for cooling high-temperature, high-pressure refrigerant to an expansion valve, and refrigerant from an accumulator to the compressor.
  • Gaseous-phase refrigerant drawn out of the accumulator is superheated by the refrigerant flowing on the high-pressure side of the internal heat exchanger, before it returns to the compressor. This enables the compressor to operate more efficiently with dry refrigerant.
  • the expansion valve is configured such that moist refrigerant is caused to flow through the bypass passage to a downstream side of the temperature-sensing section.
  • moist refrigerant is caused to flow through the bypass passage to a downstream side of the temperature-sensing section.
  • the respective bypass passage guides sufficient "wet" refrigerant to the downstream side of the temperature sensing section to lower the temperature there.
  • the description is based on refrigeration cycles using HFC-134a and an internal heat exchanger.
  • the refrigeration cycle in Fig. 1 comprises a compressor 1, a condenser 2, an expansion valve 3, and an evaporator 4.
  • An included internal heat exchanger 5 exchanges heat between refrigerant flowing from the condenser 2 to the expansion valve 3 and refrigerant flowing from the evaporator 4 to the compressor 1 via the expansion valve 3.
  • the expansion valve 3 is a so-called thermostatic expansion valve having a temperature-sensing section for sensing the temperature and pressure of refrigerant exiting the evaporator 4, and for controlling the flow rate delivered to the evaporator 4 according to the sensed temperature and pressure.
  • the expansion valve 3 internally includes either a bypass passage 3a (indicated by a solid arrow) for delivering high-pressure liquid refrigerant from the internal heat exchanger 5 to a downstream side of the temperature-sensing section, or a bypass passage 3b (indicated by a broken line arrow) for delivering low-pressure gas-liquid mixed refrigerant intended for flowing to the evaporator 4 to the downstream side of the temperature-sensing section.
  • the expansion valve 10 in Fig. 2 has the bypass passage 3a (first embodiment).
  • a body 11 is formed with a high-pressure refrigerant inlet 12 connected (high-temperature, high-pressure liquid refrigerant) to the outlet of the internal heat exchanger 5, a low-pressure refrigerant outlet 13 (low-temperature, low-pressure liquid throttled and expanded by the expansion valve 10) connected to the evaporator 4, a refrigerant passage inlet 14 connected to (evaporated refrigerant) the outlet of the evaporator 4, and a refrigerant passage outlet 15 connected to the inlet of the internal heat exchanger 5.
  • valve seat 16 In a passage between the high-pressure refrigerant inlet 12 and the low-pressure refrigerant outlet 13 a valve seat 16 is integrally formed in the body 11.
  • a ball-shaped valve element 17 is movably disposed on one side of the valve seat 16.
  • a valve element receiver 18, and a compression coil spring 19 urging the valve element 17 in valve closing direction to the valve seat 16 are arranged in a space accommodating the valve element 17.
  • a lower end of the compression coil spring 19 is supported by a spring receiver 20 which is fitted into an adjustment screw 21 screwed into a lower end of the body 11.
  • the adjustment screw 21 allows adjustments of the compression coil spring load.
  • a temperature-sensing section comprising an upper housing 22, a lower housing 23, a diaphragm 24 dividing a space enclosed by the housings, and a disk 25 disposed below the diaphragm 24.
  • a shaft 26 is disposed below the disk 25 for transmitting the displacements of the diaphragm 24 to the valve element 17.
  • An upper portion of the shaft 26 is heid by a holder 28 which extends across a refrigerant passage 27 between the refrigerant passage inlet 14 and the refrigerant passage outlet 15.
  • a compression coil spring 29 laterally loads an upper end section of the shaft 26 in the holder 28 to suppress axial vibrations of the shaft 26.
  • the body 11 contains the bypass passage 3a according to Fig. 1, in front of a separate through hole 30 through which high-pressure refrigerant may bypass the expansion valve 10.
  • the through hole 30 extends between the high-pressure refrigerant inlet 12 and the refrigerant passage 27, and contains a differential pressure control valve.
  • the differential pressure control valve comprises a valve seat 31 in the body 11, a movable valve element 32 downstream of the valve seat 31, a compression coil spring 33 urging the valve element 32 in valve-closing direction, and a spring receiver 34 for the compression coil spring 33 press-fitted into the through hole.
  • the valve element 32 is bar-shaped and has a plurality of axial peripheral communication grooves 32a. When the differential pressure control valve is opened, the high-pressure liquid refrigerant flows through the communication grooves 32a.
  • the expansion valve 10 senses pressure and temperature of refrigerant returning from the evaporator 4 via the refrigerant passage inlet 14 into the refrigerant passage 27.
  • the diaphragm 24 is displaced downward and the shaft 26 moves the valve element 17 in valve-opening direction.
  • the valve element 17 is caused to move in valve-closing direction.
  • the respective opening degree of the expansion valve 10 is controlled to control the flow rate of refrigerant to the evaporator 4, such refrigerant flowing from the evaporator 4 into the refrigerant passage 27 has a predetermined degree of superheat.
  • liquid refrigerant delivered from the evaporator 4 into the refrigerant passage inlet 14 is mixed via the through hole 30 with superheated refrigerant passing through the refrigerant passage 27.
  • the bypassing amount of liquid refrigerant is controlled according to the differential pressure between pressure in the high-pressure refrigerant inlet 12 and pressure in the refrigerant passage 27.
  • the differential pressure between discharge pressure and suction pressure in the compressor 1 is low, and hence the differential pressure between the pressure in the high-pressure refrigerant inlet 12 and the pressure in the refrigerant passage 27 is also low, such that the differential pressure control valve in the through hole 30 is closed.
  • liquid refrigerant is inhibited from directly flowing to the refrigerant passage 27 at the downstream side of the temperature-sensing section.
  • the temperature of refrigerant compressed by the compressor 1 is already not very high.
  • the differential pressures between the discharge pressure and the suction pressure in the compressor 1 and between the high-pressure refrigerant inlet 12 and the refrigerant passage 27 also increase.
  • the differential pressure across the differential pressure control valve becomes equal to a predetermined value (e.g. 1.3 MPa) or higher, the differential pressure control valve opens against the urging force of the compression coil spring 33.
  • Liquid refrigerant flows to the downstream side of the temperature-sensing section and mixes with the liquid refrigerant in the superheated state. This lowers the temperature of the refrigerant in the superheated state to thereby change the mixture into moist refrigerant.
  • the internal heat exchanger 5 causes this moist refrigerant to exchange heat with lowered-temperature refrigerant from the condenser 2, whereby the refrigerant undergoes evaporation and is superheated, and then superheated refrigerant is drawn into the compressor 1.
  • the temperature of refrigerant drawn into the compressor 1 is prevented from becoming too high, which prevents the temperature of refrigerant compressed by the compressor 1 from becoming too high. This prevents thermal deterioration of lubricating oil in the compressor 1, which oil circulates together with the refrigerant through the refrigeration cycle.
  • the through hole 30 (bypass passage 3a) is provided with an orifice 35 having a very small cross-sectional area, such that liquid refrigerant always flows through. Therefore, although the temperature of the refrigerant flowing into to the internal heat exchanger 5 can be too low when the refrigeration load is low, it is possible to reduce costs compared with the first embodiment.
  • the expansion valve 50 in Fig. 4 (third embodiment) has the through hole 30 (here the bypass passage 3b) in the body 11 between the low-pressure refrigerant outlet 13 and the refrigerant passage 27.
  • the already mentioned differential pressure control valve is also inserted into the through hole 30 in Fig. 4.
  • the spring load of the compression coil spring 33 is set such that the differential pressure control valve is opened when the differential pressure thereacross is not lower than a predetermined value of e.g. 0.03 MPa.
  • the expansion valve 60 in Fig. 5 again has the orifice 35 formed in the through hole (the bypass passage 3b).
  • the orifice 35 may be larger than in Fig. 3.
  • Gas-liquid mixed refrigerant always flows though the through hole 30 and mixes with refrigerant flowing through the refrigerant passage 27, thereby lowering the temperature of refrigerant delivered to the internal heat exchanger 5, which prevents the temperature of refrigerant compressed by the compressor 1 from becoming too high.
  • the through hole 30 (bypass passage 3b) is formed centrally and axially in the body 11 such that the shaft 26 loosely extends through the through hole 30.
  • the valve element 32 of the differential pressure control valve is axially movably disposed as a guide for the shaft 26.
  • the compression coil spring 33 is disposed between the valve element 32 and the holder 28, and urges the valve element 32 in valve closing direction to the valve seat 31 formed by a stepped transition portion to a narrower portion 30a in the through hole 30.
  • the shaft 26 passes through the narrower portion with radial clearance.
  • the expansion valve 70 operates in quite the same manner as the third embodiment.
  • the mouth of the bypass passage 3b, through which refrigerant is supplied from the through hole 30 to the refrigerant passage 27, is disposed at a location of the refrigerant passage 27, opposed to the temperature-sensing section, low-temperature gas-liquid mixed refrigerant that has been supplied from the through hole 30 to the refrigerant passage 27 through the differential pressure control valve is immediately carried away toward the refrigerant passage outlet 15 by flowing refrigerant exiting the evaporator 4, so that the gas-liquid mixed refrigerant mixes with refrigerant returning from the evaporator 4 first on the downstream side of the temperature-sensing section, without interfering with the temperature sensing function of the temperature-sensing section.
  • the through hole 30 (bypass passage 3b) is formed centrally and axially in the body 11 such that the shaft 26 loosely passes through the through hole 30.
  • the orifice 35 is also defined by the shaft 26 in the intermediate narrower portion 30a of the through hole 30.
  • the expansion valve 80 operates in the same manner as the expansion valve 60 (the fourth embodiment).
  • the expansion valve 90 in Fig. 8 (seventh embodiment) is for a refrigeration cycle employing a double tube 36 as a pipe toward the compressor 1 and the condenser 2.
  • the double tube 36 is formed by coaxially arranging an outer tube 36a and an inner tube 36b. Since refrigerant flowing through the outer tube 36a and refrigerant flowing through the inner tube 36b are separated by the inner tube 36b, the double tube 36 also fulfils the function of the internal heat exchanger 5.
  • the expansion valve 90 has the high-pressure refrigerant inlet 12 connected to the condenser 2 upstream of the valve seat 16 and the valve element 17.
  • the compression coil spring 19 and the spring receiver 20 are disposed on the downstream side of the valve element 17.
  • the through hole 30 (bypass passage 3b) is formed between a low-temperature, low-pressure chamber 17a where the valve element 17 is disposed, and the refrigerant passage 27 through which refrigerant returning from the evaporator 4 passes.
  • the valve element 32 of the differential pressure control valve is movably guided on the shaft 26 to open and close the through hole 30.
  • the valve element 32 is disposed at an open end of the through hole 30 where this opens into the refrigerant passage 27.
  • the valve element 32 is disc-shaped and has a spring collar 32a and is urged by the compression coil spring 33 to the valve seat 31.
  • High-temperature, high-pressure liquid refrigerant from the outer tube 36a to the high-pressure refrigerant inlet 12 is throttled and expanded into low-temperature, low-pressure refrigerant by passing between the valve element 17 and the valve seat 16, and is delivered from the iow-pressure refrigerant outlet 13 to the evaporator 4.
  • Refrigerant returning from the evaporator 4 is received by the refrigerant passage inlet 14, and passes through the refrigerant passage 27 to the refrigerant passage outlet 15 and into the inner tube 36b.
  • the temperature-sensing section senses the temperature and pressure of the refrigerant passing through the refrigerant passage 27, to control the flow rate of refrigerant to be delivered to the evaporator 4.
  • differential pressure control valve 31, 32 senses the differential pressure between the pressure of refrigerant in the low-pressure refrigerant outlet 13 and the pressure of refrigerant in the refrigerant passage 27, to control the flow rate through the through hole 30 between the low-pressure refrigerant outlet 13 and the refrigerant passage 27.
  • refrigerant is supplied from the through hole 30 to the refrigerant passage 27, at a location of the refrigerant passage 27, opposed to the temperature-sensing section, low-temperature gas-liquid mixed refrigerant that has been supplied from the bypass passage 30 to the refrigerant passage 27 through the differential pressure control valve is carried away toward the refrigerant passage outlet 15 by flowing refrigerant evaporated by the evaporator 4, so that the temperature of the gas-liquid mixed refrigerant is not sensed by the temperature-sensing section.

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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)
  • Air-Conditioning For Vehicles (AREA)
EP07003767A 2006-03-07 2007-02-23 Expansionsventil Not-in-force EP1832822B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006060813A JP2007240041A (ja) 2006-03-07 2006-03-07 膨張弁

Publications (3)

Publication Number Publication Date
EP1832822A2 true EP1832822A2 (de) 2007-09-12
EP1832822A3 EP1832822A3 (de) 2008-01-23
EP1832822B1 EP1832822B1 (de) 2009-01-21

Family

ID=38121651

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07003767A Not-in-force EP1832822B1 (de) 2006-03-07 2007-02-23 Expansionsventil

Country Status (6)

Country Link
US (1) US20070209387A1 (de)
EP (1) EP1832822B1 (de)
JP (1) JP2007240041A (de)
KR (1) KR20070092118A (de)
CN (1) CN101033805A (de)
DE (1) DE602007000497D1 (de)

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Publication number Priority date Publication date Assignee Title
FR2934039A1 (fr) * 2008-07-18 2010-01-22 Valeo Systemes Thermiques Boucle de climatisation amelioree pour vehicule automobile
WO2010076101A1 (de) * 2008-12-08 2010-07-08 Behr Gmbh & Co. Kg Verdampfer für einen kältekreis
DE102012224121A1 (de) * 2012-12-21 2014-06-26 Bayerische Motoren Werke Aktiengesellschaft Expansionsventil für einen Kühlkreislauf
EP2811242A1 (de) * 2013-06-07 2014-12-10 Fujikoki Corporation Expansionsventil
CZ306851B6 (cs) * 2016-03-07 2017-08-09 Hanon Systems Systém dvou koaxiálních trubic s tlakovým ventilem pro vnitřní výměník tepla a způsob chlazení pomocí takového systému
GB2550921A (en) * 2016-05-31 2017-12-06 Eaton Ind Ip Gmbh & Co Kg Cooling system
CZ308054B6 (cs) * 2010-04-16 2019-11-27 Hanon Systems Přechodový adaptér pro připojení dvou koaxiálně uspořádaných trubek k termostatickému expanznímu ventilu v klimatizačním systému
EP4063766A1 (de) * 2021-03-25 2022-09-28 Fujikoki Corporation Expansionsventil
WO2022256479A1 (en) * 2021-06-04 2022-12-08 Parker-Hannifin Corporation Bulbless expansion valve with integrated bypass check valve

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JP5501670B2 (ja) 2009-06-23 2014-05-28 株式会社不二工機 ダイアフラム式流体制御弁
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JP5713312B2 (ja) * 2010-10-28 2015-05-07 サンデン株式会社 冷凍サイクル装置
JP2012121361A (ja) * 2010-12-06 2012-06-28 Tgk Co Ltd 車両用空調装置
JP2012163281A (ja) * 2011-02-08 2012-08-30 Sanden Corp 冷凍サイクル装置
CN102221273A (zh) * 2011-06-28 2011-10-19 浙江盾安人工环境股份有限公司 丙烷空调系统热力膨胀阀
JP5445569B2 (ja) * 2011-12-09 2014-03-19 株式会社デンソー 車両用空調装置
WO2014117017A1 (en) 2013-01-25 2014-07-31 Trane International Inc. Capacity modulating an expansion device of a hvac system
DE102013113221B4 (de) * 2013-11-29 2024-05-29 Denso Automotive Deutschland Gmbh Innerer Wärmetauscher mit variablem Wärmeübergang
JP6402314B2 (ja) * 2014-12-02 2018-10-10 株式会社テージーケー 膨張弁
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JP6446636B2 (ja) * 2015-02-06 2019-01-09 株式会社テージーケー 膨張弁およびその配管取付構造
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JP6569061B2 (ja) * 2015-08-19 2019-09-04 株式会社テージーケー 制御弁
US10197177B2 (en) * 2016-03-21 2019-02-05 Ingersoll-Rand Company Compressor thermal valve unit to route lubricant used in a compressor
JP6583134B2 (ja) * 2016-05-06 2019-10-02 株式会社デンソー 冷凍サイクル装置
JP6938273B2 (ja) * 2017-08-10 2021-09-22 三菱重工サーマルシステムズ株式会社 ヒートポンプおよびその設計方法
CN111720584B (zh) * 2019-03-20 2022-09-23 浙江三花汽车零部件有限公司 一种控制阀和空调系统
JP6929318B2 (ja) * 2019-03-28 2021-09-01 東プレ株式会社 冷凍装置及び冷凍装置の運転方法
JP7599288B2 (ja) 2020-07-02 2024-12-13 日本サーモスタット株式会社 リリーフ弁、及びそれを用いた冷却回路
CN115342539A (zh) * 2021-05-14 2022-11-15 浙江三花汽车零部件有限公司 制冷系统、膨胀阀组件以及制冷系统控制方法
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Publication number Priority date Publication date Assignee Title
FR2934039A1 (fr) * 2008-07-18 2010-01-22 Valeo Systemes Thermiques Boucle de climatisation amelioree pour vehicule automobile
WO2010076101A1 (de) * 2008-12-08 2010-07-08 Behr Gmbh & Co. Kg Verdampfer für einen kältekreis
US8616012B2 (en) 2008-12-08 2013-12-31 Behr Gmbh & Co. Kg Evaporator for a refrigeration circuit
CZ308054B6 (cs) * 2010-04-16 2019-11-27 Hanon Systems Přechodový adaptér pro připojení dvou koaxiálně uspořádaných trubek k termostatickému expanznímu ventilu v klimatizačním systému
DE102012224121A1 (de) * 2012-12-21 2014-06-26 Bayerische Motoren Werke Aktiengesellschaft Expansionsventil für einen Kühlkreislauf
EP2811242A1 (de) * 2013-06-07 2014-12-10 Fujikoki Corporation Expansionsventil
CZ306851B6 (cs) * 2016-03-07 2017-08-09 Hanon Systems Systém dvou koaxiálních trubic s tlakovým ventilem pro vnitřní výměník tepla a způsob chlazení pomocí takového systému
GB2550921A (en) * 2016-05-31 2017-12-06 Eaton Ind Ip Gmbh & Co Kg Cooling system
CN109477674A (zh) * 2016-05-31 2019-03-15 伊顿智能动力有限公司 冷却系统
EP4063766A1 (de) * 2021-03-25 2022-09-28 Fujikoki Corporation Expansionsventil
WO2022256479A1 (en) * 2021-06-04 2022-12-08 Parker-Hannifin Corporation Bulbless expansion valve with integrated bypass check valve

Also Published As

Publication number Publication date
EP1832822B1 (de) 2009-01-21
CN101033805A (zh) 2007-09-12
EP1832822A3 (de) 2008-01-23
JP2007240041A (ja) 2007-09-20
KR20070092118A (ko) 2007-09-12
US20070209387A1 (en) 2007-09-13
DE602007000497D1 (de) 2009-03-12

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