US20170045273A1 - Cryogenic refrigeration system - Google Patents

Cryogenic refrigeration system Download PDF

Info

Publication number
US20170045273A1
US20170045273A1 US15/305,911 US201515305911A US2017045273A1 US 20170045273 A1 US20170045273 A1 US 20170045273A1 US 201515305911 A US201515305911 A US 201515305911A US 2017045273 A1 US2017045273 A1 US 2017045273A1
Authority
US
United States
Prior art keywords
refrigerant
heat exchanger
refrigeration system
cryogenic
disposed
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.)
Abandoned
Application number
US15/305,911
Other languages
English (en)
Inventor
Woo Suk Chung
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.)
Sunam Co Ltd
Original Assignee
Sunam 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 Sunam Co Ltd filed Critical Sunam Co Ltd
Priority claimed from PCT/KR2015/004044 external-priority patent/WO2015163703A1/ko
Assigned to SUNAM CO., LTD. reassignment SUNAM CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHUNG, WOO SUK
Publication of US20170045273A1 publication Critical patent/US20170045273A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1428—Control of a Stirling refrigeration machine
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—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 disclosed herein relates to a cryogenic refrigeration system, and more particularly, to a cryogenic refrigeration system capable of improving a coefficient of performance thereof.
  • a cryogenic refrigerator may be used to cool a superconductor or a small-sized electronic component.
  • the cryogenic refrigerator may include a stifling refrigerator, a GM refrigerator, and a Joule-Thomson refrigerator.
  • the above-described cryogenic refrigerator may generate refrigeration output through an expansion process of working fluid such as helium or hydrogen. The expansion process may accompany heat generation of a compression process.
  • the cryogenic refrigerator may be cooled by a heat dissipater.
  • the typical cryogenic refrigerator may be cooled by a dual heat dissipater.
  • the dual heat dissipater may include a water-cooling type heat dissipater and a vapor compression refrigerator.
  • the water-cooling type radiator may cool the cryogenic refrigerator.
  • the water-cooling type heat dissipater may be cooled by the vapor compression refrigerator However, since the water-cooling type heat dissipater uses water that has a low cooling efficiency of performance, a coefficient of performance of the cryogenic refrigerator may be reduced. In addition, the water-cooling type heat dissipater and the vapor compression refrigerator may increase costs for operating the cryogenic refrigerator to reduce productivity.
  • the present invention provides a cryogenic refrigeration system capable of increasing a radiant efficiency due to a coefficient of performance of refrigerant.
  • the present invention also provides a cryogenic refrigeration system capable of minimizing costs for operating a cryogenic refrigerator.
  • Embodiments of the present invention provide a cryogenic refrigeration system including: a cryogenic refrigerator; and a heat dissipation module configured to cool the cryogenic refrigerator.
  • the heat dissipation module includes: a condenser spaced apart from the cryogenic refrigerator to condense a refrigerant that cools the cryogenic refrigerator; and a heat exchanger connected to the cryogenic refrigerator to circulate the refrigerant between the cryogenic refrigerator and the condenser, thereby cooling the cryogenic refrigerator.
  • cryogenic refrigeration systems include: a cryogenic refrigerator comprising a power generation part, a power conversion part configured to convert power generated in the power generation part, and a gas cooling part configured to cool a gas by using the power converted in the power conversion part; and a heat dissipation module configured to circulate a refrigerant that cools the cryogenic refrigerator into the power generation part, the power conversion part, and the gas cooling part.
  • the cryogenic refrigeration system may use refrigerant having a coefficient of performance and/or a heat absorption efficiency greater than that of the water to increase a radiant efficiency of the cryogenic refrigerator.
  • the cryogenic refrigerator may be directly cooled by the heat dissipation module to minimize the operational costs.
  • FIG. 1 is a diagram illustrating an example of a cryogenic refrigeration system according to the present invention.
  • FIG. 2 is a diagram illustrating a cryogenic refrigerator in FIG. 1 .
  • FIG. 3 is a diagram illustrating another example of the cryogenic refrigeration system in FIG. 1 .
  • FIG. 4 is a diagram illustrating still another example of the cryogenic refrigeration system in FIG. 1 .
  • FIG. 1 is a diagram illustrating an example of a cryogenic refrigeration system 10 according to the present invention.
  • FIG. 2 is a diagram illustrating a cryogenic refrigerator 100 in FIG. 1 .
  • the cryogenic refrigeration system 10 may include the cryogenic refrigerator 100 and a heat dissipation module 200 .
  • the cryogenic refrigerator 100 may be cooled to a cryogenic temperature.
  • the heat dissipation module 200 may dissipate heat from the cryogenic refrigerator 100 .
  • the cryogenic refrigerator 100 may include a sterling cryogenic refrigerator. According to an embodiment, the cryogenic refrigerator 100 may include a power generation part 110 , a power conversion part 120 , and a gas cooling part 130 .
  • the power generation part 110 may generate rotational power by external power.
  • the power generation part 110 may include a motor.
  • the power generation part 110 may be connected to the power conversion part 120 .
  • the power generation part 110 may be heated to a temperature greater than a room temperature.
  • the power generation part 110 may be heated to a temperature equal to or greater than about 30° C.
  • the power conversion part 120 may convert the rotational power to reciprocating linear power.
  • the power conversion part 120 may include a shaft 1 cam 125 , a plurality of connecting rods 126 , and a housing 128 .
  • the shaft 122 may be connected to the power generation part 110 .
  • the cam 124 may be connected between the shaft 122 and the connecting rods 126 .
  • the connecting rods 126 may extend to the gas cooling part 130 .
  • the housing 128 may surround the cam 124 .
  • the housing 128 may be connected to the gas cooling part 130 .
  • the housing 121 may be provided in the housing 128 . Oil 121 may be heated by operation of the shaft 122 , the cam 124 , and the connecting rods 126 .
  • the gas cooling part 130 may be disposed on the power conversion part 120 .
  • the gas cooling part 130 may cool gas 131 at the cryogenic temperature.
  • the gas 131 may include helium gas.
  • the gas cooling part 130 may include a cylinder 132 , a displacer 140 , and a piston 150 .
  • the cylinder 132 may be connected onto the power conversion part 120 .
  • the gas 131 may be provided into the cylinder 132 .
  • the displacer 140 and the piston 150 may be connected to the connecting rods 126 to move up and down in the cylinder 132 .
  • the displacer 140 may be disposed above the pistol 150 .
  • One of the connecting rods 126 may pass through the piston 150 .
  • the cylinder 132 may include a gas expansion region 134 , a gas compression region 136 , and a piston movement region 138 .
  • the gas expansion region 134 may be disposed above the gas compression region 136 .
  • the displacer 140 may be connected to one of the connecting rods 126 to move up and down in the gas expansion region 134 and the gas compression region 136 .
  • the displacer 140 may expand and cool the gas 131 in the gas expansion region 134 .
  • the gas expansion region 134 may be a cooling region.
  • the gas compression region 136 may be connected to the rest of the connecting rods 126 and disposed between the gas expansion region 134 and the piston movement region 138 .
  • the piston 150 may move up and down in the piston movement region 138 .
  • the piston movement region 138 may be a region through which one of the connecting rods 126 passes.
  • the displacer 140 and the piston 150 may compress the gas 131 in the gas compression region 136 .
  • the compressed gas 131 may heat the cylinder 132 in the gas compression region 136 .
  • the gas compression region 136 may be a heating region.
  • the heat dissipation module 200 may circulate to supply refrigerant to the power generation part 110 , the power conversion part 120 , and the gas cooling part 130 to directly cool the cryogenic refrigerator 100 .
  • the direct cooling method may have a size smaller than that of the typical dual heat dissipater and reduce maintenance costs. Accordingly, the cryogenic refrigeration system 10 according to the present invention may reduce the operational costs.
  • the heat dissipation module 200 may include a condenser 210 , a compressor 220 , heat exchangers 230 , a refrigerant expander 240 , a refrigerant supply line 250 , and a refrigerant collecting line 260 .
  • the condenser 210 may condense the refrigerant.
  • the compressor 220 may be connected to the condenser 210 .
  • the condenser 220 may compress the refrigerant.
  • the refrigerant may include R22, R123, R134a, HFC-407C, HFC-407A, or R-123yf.
  • the refrigerant may have a freezing point and an evaporation point, which are lower than those of water.
  • the water may have a coefficient of performance (COP) of about 0.2625.
  • the refrigerant of the R22 may have the coefficient of performance greater than that of the water.
  • the R22 at a temperature of about ⁇ 30° C. is heat-exchanged to about ⁇ 15° C.
  • the R22 may have the coefficient of performance of about 0.323.
  • the heat exchangers 230 may be connected to the power generation part 110 , the power conversion part 120 , and the gas cooling part 130 .
  • the refrigerant supply line 250 may be connected between the condenser 210 and the heat exchangers 230 .
  • a radiant efficiency of the cryogenic refrigerator 100 may be increased.
  • the refrigerant expander 240 may be connected to the refrigerant supply line 250 .
  • the refrigerant collecting line 260 may be connected between the compressor 220 and the heat exchangers 230 .
  • the condenser 210 may liquefy the refrigerant.
  • the condenser 210 may include a water-cooling type condenser and an air-cooling type condenser.
  • the refrigerant expander 240 may be disposed between the condenser 210 and the heat exchangers 230 .
  • the refrigerant expander 240 may vaporize and cool the refrigerant.
  • the cooled refrigerant may be supplied to the heat exchangers 230 through the refrigerant supply line 250 ,
  • the refrigerant may be heated in the heat exchangers 230 .
  • the compressor 220 may supply the heated refrigerant to the condenser 210 with a predetermined pressure.
  • the refrigerant in a gas state may be supplied to the condenser 210 .
  • the refrigerant may be circulated between the heat exchangers 230 and the condenser 210 .
  • the heat exchangers 230 may cool the power generation part 110 , the power conversion part 120 , and the gas cooling part 130 .
  • the heat exchangers 230 may include a gas heat exchanger 232 , an oil heat exchanger 234 , and a motor heat exchanger 236 .
  • the gas heat exchanger 232 may be disposed in the compression region 136 .
  • the gas heat exchanger 232 may cool the cylinder 132 in the compression region 136 .
  • the heat exchange supply line 233 may connect the gas heat exchanger 232 to the oil heat exchanger 234 .
  • the heat exchange collecting line 235 may connect the gas heat exchanger 232 to the motor heat exchanger 236 .
  • the refrigerant may be sequentially supplied to the oil heat exchanger 234 , the gas heat exchanger 232 , and the motor heat exchanger 236 .
  • a first protection cover 312 may be disposed to surround the gas heat exchanger 232 .
  • the first protection cover 312 may protect the gas heat exchanger 232 .
  • the first protection cover 312 may prevent dew formation caused by cooling of the gas heat exchanger 231 .
  • the power generation part 234 may be disposed on the power conversion part 120 .
  • the oil heat exchanger 234 may cool the oil in the power conversion part 120 .
  • the oil heat exchanger 234 may be connected to the refrigerant supply tine 250 .
  • a second protection cover 314 may be disposed to surround the heat exchanger 234 .
  • the second protection cover 314 may protect the oil heat exchanger 234 .
  • the motor heat exchanger 236 may be disposed on the power generation part 110 .
  • the motor heat exchanger 236 may cool the power generation part 110 .
  • the motor heat exchanger 236 may be connected to the refrigerant collecting line 260 .
  • FIG. 3 is a diagram illustrating another example of the cryogenic refrigeration system 10 in FIG. 1 .
  • the heat dissipation module 200 may include a first pressure transducer 272 , a first temperature sensor 274 , and a circulation flow rate controller 276 .
  • the first pressure transducer 272 may be disposed in the refrigerant collecting line 260 between the heat exchangers 230 and the compressor 220 .
  • the first pressure transducer 272 may detect a pressure of the refrigerant.
  • the first temperature sensor 274 may be disposed in the refrigerant collecting line 260 disposed adjacent to the first pressure transducer 272 .
  • the first temperature sensor 274 may detect a temperature of the refrigerant.
  • the circulation flow rate controller 276 may be connected to the first pressure transducer 272 , the first temperature sensor 274 , and the refrigerant expander 240 . Also, the circulation flow rate controller 276 may receive a detection signal of the temperature and the pressure of the first pressure transducer 272 and the first temperature sensor 274 . The circulation flow rate of the refrigerant may be controlled on the basis of the temperature and the pressure. The refrigerant expander 240 may control the circulation flow rate of the refrigerant according to the control signal of the circulation flow rate controller 276 .
  • the cryogenic refrigerator 100 and the condenser 210 , the compressor 220 , the heat exchangers 230 , the refrigerant expander 240 , the refrigerant supply line 250 , and the refrigerant collecting line 260 of the heat dissipation module 200 may be the same as those in FIGS. 1 and 2 .
  • FIG. 4 is a diagram illustrating still another example of the cryogenic refrigeration system 10 in FIG. 1 .
  • the heat dissipation module 200 may include a second temper sensor 282 , a second pressure transducer 284 , a bypass valve 286 , a bypass controller 288 , a bypass line 290 , and a sensitive heat tube 292 .
  • the second temperature sensor 282 may be disposed in the refrigerant collecting line 260 .
  • the second temperature sensor 282 may detect the temperature of the refrigerant.
  • the second pressure transducer 284 may be disposed in the refrigerant collecting line 260 .
  • the second pressure transducer 284 may detect the pressure of the refrigerant.
  • the bypass valve 286 may be disposed in the refrigerant collecting line 260 between the condenser 210 and the compressor 220 .
  • the bypass valve 286 may be connected to the bypass line 290 .
  • the bypass valve 286 may include a three-way valve.
  • the bypass controller 288 may control the bypass valve 286 .
  • the bypass controller 288 may receive temperature and pressure signals of the second temperature sensor 282 and the second pressure transducer 284 .
  • the bypass line 290 may detour the condenser 210 to connect the refrigerant collecting line 260 to the refrigerant supply line 250 .
  • the bypass line 290 may be branched from the bypass valve 286 .
  • the bypass line 290 may be connected to the refrigerant supply line 250 between the heat exchangers 230 and the refrigerant expander 240 .
  • the bypass controller 288 may allow the refrigerant to detour from the refrigerant collecting line 260 to the refrigerant supply line 250 through the bypass line 290 .
  • the bypass controller 288 may allow the refrigerant to detour from the refrigerant collecting line 260 to the refrigerant supply line 250
  • the sensitive heat tube 292 may be disposed in the refrigerant collecting line 260 , The sensitive heat tube 292 may be connected to the refrigerant expander 240 .
  • the sensitive heat tube 292 may detect the temperature of the refrigerant in the refrigerant collecting line 260 .
  • the sensitive heat tube 292 regulates the refrigerant expander 240 on the basis of the temperature of the refrigerant.
  • the sensitive heat tube 292 may output a turn-on signal and a turn-off signal of the refrigerant expander 240 . When the temperature of the refrigerant is high, the sensitive heat tube 292 may output the turn-on signal. When the temperature of the refrigerant is low, the sensitive heat tube 292 may output the turn-off signal.
  • the cryogenic refrigerator 100 and the condenser 210 , the compressor 220 , the heat exchangers 230 , the refrigerant expander 240 , the refrigerant supply line 250 , and the refrigerant collecting line 260 of the heat dissipation module 200 may be the same as those in FIGS. 1 and 2 .
  • the cryogenic refrigerator may increase the radiant efficiency thereof to minimize the operational costs.
  • the cryogenic refrigerator may effectively cool the low temperature superconductor or high temperature superconductor.
  • the superconductor may be used as a source material for a power plant, a substation, a magnetic resonance device, a magnetic levitation train, a superconductor research center.
  • the cryogenic refrigerator may be widely used in the field of superconductor technology.
  • the cryogenic refrigerator may be mounted on a tensile tester for cryogenic metal.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
US15/305,911 2014-04-25 2015-04-23 Cryogenic refrigeration system Abandoned US20170045273A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
KR20140050248 2014-04-25
KR10-2014-0050248 2014-04-25
KR10-2015-0052640 2015-04-14
KR1020150052640A KR20150124390A (ko) 2014-04-25 2015-04-14 극저온 냉동 시스템
PCT/KR2015/004044 WO2015163703A1 (ko) 2014-04-25 2015-04-23 극저온 냉동 시스템

Publications (1)

Publication Number Publication Date
US20170045273A1 true US20170045273A1 (en) 2017-02-16

Family

ID=54600605

Family Applications (1)

Application Number Title Priority Date Filing Date
US15/305,911 Abandoned US20170045273A1 (en) 2014-04-25 2015-04-23 Cryogenic refrigeration system

Country Status (5)

Country Link
US (1) US20170045273A1 (ko)
EP (1) EP3136021A4 (ko)
JP (1) JP2017514101A (ko)
KR (1) KR20150124390A (ko)
CN (1) CN106461285A (ko)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4265987A1 (en) * 2022-04-21 2023-10-25 Bluefors Oy Cryostat, and method for cooling a cryostat

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5963465A (ja) * 1982-10-05 1984-04-11 松下電器産業株式会社 熱力学往復動冷凍機関
KR20000052196A (ko) * 1999-01-30 2000-08-16 구자홍 무윤활 맥동관 냉동기의 냉각장치
US20110100031A1 (en) * 2009-11-04 2011-05-05 Emidio Barsanti Device and method for operating a refrigeration cycle with noncondensable gas addition.
US20140000235A1 (en) * 2009-07-01 2014-01-02 Deka Products Limited Partnership Stirling cycle machine

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2551000B2 (ja) * 1987-05-29 1996-11-06 アイシン精機株式会社 極低温発生装置
JPH0733932B2 (ja) * 1989-04-28 1995-04-12 ダイキン工業株式会社 極低温冷凍機用のヘリウム圧縮装置
JPH06159838A (ja) * 1992-11-30 1994-06-07 Sanden Corp スターリングサイクル冷凍機
JP3949135B2 (ja) * 2004-11-17 2007-07-25 シャープ株式会社 圧電ポンプおよびスターリング冷却庫
JP4718957B2 (ja) * 2005-09-29 2011-07-06 株式会社東芝 パルスチューブ冷凍機
JP2008249157A (ja) * 2007-03-29 2008-10-16 Saginomiya Seisakusho Inc 可逆温度式膨張弁
JP2009264688A (ja) * 2008-04-28 2009-11-12 Hitachi Ltd 鉄道車両用空調装置
CN201909486U (zh) * 2010-12-13 2011-07-27 泰豪科技股份有限公司 利用热气旁通调节阀解决机组低负荷运行的空调装置
JP2012202672A (ja) * 2011-03-28 2012-10-22 Mitsubishi Heavy Ind Ltd 膨張弁制御装置、熱源機、及び膨張弁制御方法
CN203501316U (zh) * 2013-05-08 2014-03-26 艾默生网络能源有限公司 空调系统

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5963465A (ja) * 1982-10-05 1984-04-11 松下電器産業株式会社 熱力学往復動冷凍機関
KR20000052196A (ko) * 1999-01-30 2000-08-16 구자홍 무윤활 맥동관 냉동기의 냉각장치
US20140000235A1 (en) * 2009-07-01 2014-01-02 Deka Products Limited Partnership Stirling cycle machine
US20110100031A1 (en) * 2009-11-04 2011-05-05 Emidio Barsanti Device and method for operating a refrigeration cycle with noncondensable gas addition.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
KR 196 the applicant 12/6/17 - *

Also Published As

Publication number Publication date
CN106461285A (zh) 2017-02-22
JP2017514101A (ja) 2017-06-01
KR20150124390A (ko) 2015-11-05
EP3136021A1 (en) 2017-03-01
EP3136021A4 (en) 2018-05-02

Similar Documents

Publication Publication Date Title
KR101330193B1 (ko) 냉동 장치 및 이와 관련된 냉매를 순환시키는 방법
US20110088419A1 (en) Thermodynamic Cycle for Cooling a Working Fluid
JP4989905B2 (ja) 廃熱利用システム
JP2010501826A (ja) 通信装備用冷房装置
CN105539123B (zh) 一种电动汽车冷却系统
KR19980080394A (ko) 가스 터빈 흡기 냉각장치
JP2007178072A (ja) 車両用空調装置
EP3217116A1 (en) Recovery of heat generated by compressor driver
US2386198A (en) Multistage refrigerating system
JP6665003B2 (ja) コージェネレーション装置
US6330809B1 (en) Application of a chiller in an apparatus for cooling a generator/motor
JP2014085048A (ja) ターボ冷凍機
US20170045273A1 (en) Cryogenic refrigeration system
JP2018159507A (ja) Ｇｈｐチラー
JP2007051788A (ja) 冷凍装置
CN103322662B (zh) 采用热风扩展工作温度并具有独立双换热回路的制冷系统
KR20090095744A (ko) 냉각장치
CN210128524U (zh) 一种用于内藏式展示柜的多级换热风冷散热系统
CN210292407U (zh) 高低温冲击试验箱及其制冷系统
CN104930890B (zh) 一种热交换器及半导体酒柜
WO2018100711A1 (ja) 冷凍装置
WO2015163703A1 (ko) 극저온 냉동 시스템
JP2005030708A (ja) 地中熱ヒートポンプ制御用半導体の冷却構造
CN215808805U (zh) 一种复合热回收系统
JP2006284062A (ja) 超電導電力貯蔵装置冷却用極低温冷却装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: SUNAM CO., LTD., KOREA, REPUBLIC OF

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CHUNG, WOO SUK;REEL/FRAME:040278/0929

Effective date: 20161104

STPP Information on status: patent application and granting procedure in general

Free format text: FINAL REJECTION MAILED

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION