US3447339A - Cold producing systems - Google Patents

Cold producing systems Download PDF

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Publication number
US3447339A
US3447339A US637960A US3447339DA US3447339A US 3447339 A US3447339 A US 3447339A US 637960 A US637960 A US 637960A US 3447339D A US3447339D A US 3447339DA US 3447339 A US3447339 A US 3447339A
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United States
Prior art keywords
reservoir
medium
pressure
ejector
heat
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Expired - Lifetime
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US637960A
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English (en)
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Johan Adriaan Rietdijk
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US Philips Corp
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US Philips Corp
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    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0275—Construction and layout of liquefaction equipments, e.g. valves, machines adapted for special use of the liquefaction unit, e.g. portable or transportable devices
    • F25J1/0276—Laboratory or other miniature devices
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/0052—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
    • F25J1/0062—Light or noble gases, mixtures thereof
    • F25J1/0065—Helium
    • 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
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low 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
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high 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
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0015—Ejectors not being used as compression device using two or more ejectors
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/90—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration
    • F25J2270/912—Liquefaction cycle of a low-boiling (feed) gas in a cryocooler, i.e. in a closed-loop refrigerator

Definitions

  • This invention relates to a cold producing apparatus for cooling an electronic element including its current conductors which extend to a higher temperature environment and produce heat during operation of the element.
  • the apparatus includes means for compressing a fluid medium, a heat exchanger for initial cooling of the medium to a temperature below its inversion temperature, an ejector for expanding and cooling the medium to a lower intermediate temperature and pressure, and a first reservoir for receiving said expanded medium and conducting it through a choke to a second reservoir at a lower temperature and pressure.
  • the invention relates to a cold producing system for cooling devices such as cryogenic storage elements or memories, calculating elements of electronic computers, and coils, which operate at very low temperatures. Cooling of these devices during their operation is required because of the heat produced internally and heat resulting from their contact with current connectors or other heat conducting connections.
  • the elements operating at a very low temperature are arranged in a bath containing a liquid such as helium, boiling at a low temperature.
  • the desired operational temperature of these elements is usually on the order of 3 K. and less, and these temperatures are related to vapour pressures of helium of about 0.25 ata. and less.
  • a quantity of heat will pass from the environments of higher temperature to the elements operating at the lower temperature. Due to this penetrating heat and the developed heat respectively, a quantity of helium will be evaporated in the bath.
  • the invention has for its object to obviate the aforesaid disadvantages and is characterized in that the cold producing member comprises a compression member for compressing a medium, the outlet of compressed medium communicating with one or more heat exchangers in which the compressed medium is cooled to below the inversion temperature associated with the medium pressure.
  • the system further comprises at least one ejector to which the cooled high-pressure medium can be supplied. The outlet of each ejector communicates lower pressure medium to a first reservoir which communicates via one outlet through a heat exchanger to the suction side of the compression member.
  • This first reservoir also communicates via a second outlet through a choking member to a second reservoir in which lower pressures prevail than in the outlet or the first reservoir, and the additional reservoir communicates through a heat exchanger with the suction side of an ejector.
  • the said cooled elements operating at a very low temperature are disposed in thermal contact or with at least the second reservoir in which the lowest pressure prevails, while the current conductors or the other heat-conducting connections are in thermal contact with the outlet of the ejector, the first reservoir, if used, or the medium contained therein, and with the further reservoir in which the lowest pressure prevails.
  • an ejector is to denote a device in which the potential energy of a highpressure (primary) medium is converted wholly or partly into kinetic energy, which is used at least partly for raising the pressure of a second (secondary) medium.
  • the energy of the high-pressure medium supplied to each of the ejectors is utilized at least partly for drawing off the vapour from the 'further low-pressure reservoir or reservoirs, and to compress this vapour to the pressure prevailing in the ejectors outlet or the pressure in the first reservoir communicating with the suction side of the compressor.
  • the suction pressure of the compressor is therefore no longer equal to the pressure prevailing in the second reservoir in which are arranged the elements operating at a very low temperature, but it is equal to the higher pressure prevailing in the outlet of the ejector.
  • the elements operating at the low temperature are connected via current conductors and other heat-conducting connections to environments of higher temperature, and these connections a given flow of heat will be conducted towards the elements.
  • this penetrating heat has to be compensated, which is achieved by the evaporation of part of the condensate of the reservoir and by the removal of this vapour from the reservoir.
  • the current conductors and the further heatconducting connections were in direct contact with the elements operating at low temperature, the whole ilow of penetrating heat would be received in the reservoir in which the elements are arranged and in which the lowest temperature prevails. This produces a development of vapour in this reservoir. In order to maintain the desired temperature and pressure in this reservoir the vapour has to be drawn off by the ejector.
  • the ejector is capable of converting the expansion power of the primary medium with a given efficiency into compressive power for the secondary medium, with efficiencies of conventional ejectors being about 25%. If in a given case a predetermined primary flow of a mass with a given temperature is available, and if it is desired to maintain a given pressure in the reservoir to be emptied at the in-flow of a given quantity of heat, a given pressure will be produced in the first reservoir which communicates with the outlet side of the ejector.
  • the current conductors and other heat-conducting connections are first brought into thermal contact with the outlet of the ejector or the first reservoir, a great portion of the penetrating heat will be captured at this place. Consequently, less vapour will be developed in the reservoir to be emptied, which means that the efficiency of the ejector may be lower. If the etficiency of the ejector remains the same, the pressure in the first reservoir may be higher. This means that the suction pressure of the compressor will be higher, so that the compression ratio is lower and the efiiciency of the system is higher.
  • FIGURES 1, 2 and 3 show diagrammatically, not to scale, three embodiments of cold producing systems.
  • reference numeral 1 designates a compressor.
  • the compressed medium is first passed through a cooler 2, in which the compressive heat is conducted away.
  • the compressed medium then flows through a heat exchanger 3, where it exchanges heat with a lowerpressure medium.
  • the high-pressure medium is subsequently cooled in a heat exchanger 4 by means of a cooler 5 to a temperature of, for example, 60 K.
  • the high-pressure medium then flows through a heat exchanger 6, where it exchanges heat with a lower-pressure medium.
  • the high-pressure medium is cooled in a heat exchanger 7 with the raid of the cooler 8 to a temperature of, for example, K., and in the heat exchanger 9 it exchanges heat with expanded medium.
  • the temperature of the high-pressure medium is then below the inversion temperature of the medium at the prevailing pressure.
  • the medium then enters an ejector 10, in which its pressure is reduced.
  • the ejector communicates with an outlet 11, and to a reservoir 12.
  • the vapour space of the reservoir 12 communicates via the heat exchangers 9, 6 and 3 with the inlet side of the compressor 1.
  • the condensate of the reservoir 12 can flow via the heat exchanger 13- and the choking cock 14 in which the pressure of the liquid is further reduced, to the reservoir 15 in which a lower pressure prevails than in the reservoir 12.
  • the vapour space of the reservoir 15 communicates through the heat exchanger 13 with the suction side 16 of the ejector 10.
  • the reservoir 15 accommodate a cryogenic memory element 17 of an electronic computer, connected through current conductors (two of them 18 and 19 are shown) to an environment of higher temperature.
  • the medium in this system is helium, and for satisfactory operation of the memory 17, it is desirable to maintain its temperature at about 3 K., which is associated with a vapour pressure of helim of about 0.25 ata.
  • the current conductors 18 and 19 are connected at one end to an environment of ambient temperature and at the other end to the memory 17 at 3 K. Owing to the difference in temperature heat will leak into the memory. When current passes, Joules heat will be developed in the current conductors. Above the plane II the current conductors are in thermal contact with the medium in the heat exchangers 3, 4, 6, 7 and 9. After the last cooler the current conductors could enter the memory 17 without exchange of heat. This means that along the last portion of the current conductors a temperature gradient from 15 K. to 3 K. would prevail, so that a given quantity of heat might leak away towards the reservoir 15. This quantity of heat is compensated by the evaporation of a 4 given quantity of helium in the reservoir 15.
  • the developed vapour has to be removed from the reservoir 15, which is achieved by the ejector 10, the suction side of which communicates with the reservoir 15.
  • the ejector converts the potential energy of the high-pressure medium into energy employed for drawing off vapour from the reservoir 15 and for com pressing it to the pressure prevailing in the reservoir 15.
  • the pressure in the reservoir 12 will be lower according as a larger quantity of vapour has to be withdrawn from the reservoir 15.
  • a low pressure in the reservoir 12 is harmful for the system, since the heat exchangers are then constructurally more complicated and the compressor must have greater dimensions and a higher compression ratio.
  • the current conductors 18 and 19 of the cold producing system of FIGURE 1 are also in thermal contact with the helium in the reservoir 12 and/ or with the heat exchanger. This has the advantage that a great portion of the heat leaking away towards the lowest temperature is absorbed already at the temperature of the reservoir 12, so that the quantity of vapour to be withdrawn from the reservoir 15 is smaller, which results in a higher pressure in the reservoir 12. This involves the advantage that the compressor and the compression ratio may be smaller, which provides a structural simplification and an economy of power.
  • FIGURE 1 comprises a reservoir 12 at the outlet 11 of the ejector, this reservoir may be dispensed with, so that at this place the outlet 11 directly splits up into a duct towards the heat exchanger 9 and a duct to the heat exchanger 13.
  • the current conductors can then be in direct thermal contact with the outlet 11.
  • the compressor may, of course, be of ,any conventional type independently of the compression ratio in one or more stages.
  • the coolers 8 and 9 may be formed by the freezers of a two-stage Stirling cold-gas refrigerator, or other coolers may be employed. It is possible, for example, to use as coolers expansion turbines, in which a portion of the high-pressure medium is expanded to the suction pressure of the compressor. In this case the compressor serves as a driver for the coolers 8 and 9 and the ejector, in which the advantage of the higher suction pressure obtainable by an ejector system, and particularly by the system of the present invention, is of very great advantage.
  • FIGURE 1 comprises only one ejector
  • the invention may, of course, be applied to cold producing systems comprising a plurality of ejectors.
  • FIGURE 2 shows diagrammatically a cold producing system comprising two series-connected ejectors 20 and 21, and a heat exchanger 20a disposed between the ejectors.
  • the reservoir 12 communicates through a heat eX- changer 22 and a choking cock 23 with a further reservoir 24, which communicates through the heat exchanger 13 and the choking cock 14 with the reservoir 15, in which the memory 17 is disposed.
  • the vapour spaces of the reservoirs 24 and 15 communicate with the suction sides of the ejectors 21 and 20 respectively.
  • the current conductors 18 and 19 are in thermal contact with the reservoirs 12, 24, and 15, which provides the above-described advantages. The operation of this system will be obvious, as it corresponds to that of FIG. 1.
  • FIGURE 3 shows diagrammatically a cold producing system comprising two parallel-connected ejectors 30 and 31. These ejectors both communicate with the highpressure side of the heat-exchanger 9, and with heat exchanger 9a.
  • the outlet 11 of the ejector 30 communicates with the reservoir 12, and the outlet 32 of the ejector 3-1 communicates with a further reservoir 33.
  • the reservoir 12 communicates with the reservoir 33, the latter communicating through the heat exchanger 13 and the choking cock 14 with the reservoir 15 accomodating the memory 17.
  • the current conductors 18 and 19 are in thermal contact with the medium in the reservoirs 12 and 33 so that the major portion of the heat flowing in the direction of the memory 17 is absorbed at higher temperature levels.
  • the invention provides a cold producing system including one or more ejectors, wherein heat is transferred with a high degree of efiiciency from an environment at very low temperature to a place of higher temperature.
  • a cold producing apparatus for maintaining at least one electronic element therein at a relatively low temperature, said element being provided with current conductors which produce heat and are connected to locations at higher temperatures; the improvement comprising a means for compressing a medium, a plurality of heat exchangers in which the compressed medium is cooled to below the inversion temperature associated with the pressure of said medium, at least one ejector to which said cooled high pressure medium is supplied, a reservoir having the lowest pressure of the apparatus, a choking member, the outlet of said ejector having two branches, the first communicating fluid through said choking member to said reservoir, said reservoir communicating with the suction side of said ejector, the second branch communicating fluid through said heat exchangers to the suction side of the compressor, said electronic element operating at a low temperature being in thermal contact with said reservoir, and the current conductors of said element being in thermal contact with at least the outlet of said ejector and said reservoir.
  • a cold producing apparatus for cooling an electronic element to a relatively low temperature, the element being connected to current conductors which extend to a higher temperature environment and produce heat during operation of the element comprising:
  • At least one ejector having (1) a first inlet for receiving from the heat exchanger cooled medium in a gaseous state, which medium is expandable in the ejector to a second intermediate temperature and pressure below that in the heat exchanger, (2) an outlet through which expanded medium is dischargeable, and (3) a suction inlet for pumping medium therein,
  • Apparatus as defined in claim 2 further comprising a second heat exchanger wherein medium flowing between the first reservoir and choke means is cooled by medium flowing between the second reservoir and the suction inlet of the ejector.
  • Apparatus as defined in claim 2 further comprising (a) a second choke, (b) a second ejector similar to and disposed in series with said first ejector between said first ejector and said first heat exchanger, (c) a third reservoir having an outlet connected to the suction inlet of the second ejector and an inlet, said second reservoir having a second outlet connected through said second choke to the inlet of said third reservoir, and (d) third means for thermal contact between said current conductors and medium in said third reservoir.
  • Apparatus as defined in claim 2 further comprising: (a) a second ejector similar to and disposed in parallel with the first ejector, (b) a third reservoir and an associated choke disposed in series between said first heat exchanger and first reservoir, the third reservoir having an inlet connected to the outlet of said second ejector and an outlet connected to said first reservoir, the first reservoir having an additional outlet connected to the suction inlet of said second ejector, and ((1) third means for thermal contact between said current conductors and medium in said third reservoir.
  • a cold producing apparatus for maintaining an electronic element at a relatively low temperature, the element being connected to current conductors which produce heat and extend to a higher temperature environment; the improvement comprising:
  • a first reservoir having (1) an inlet for receiving low pressure medium from said ejector, (2) a first outlet communicating with said compressing means, and (3) a second outlet;
  • a second reservoir having an inlet for receiving expanded medium from said choke means, and an outlet for communicating vapor therein to the suction outlet of an ejector;

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Health & Medical Sciences (AREA)
  • Clinical Laboratory Science (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US637960A 1966-05-25 1967-05-12 Cold producing systems Expired - Lifetime US3447339A (en)

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NL6607168A NL6607168A (zh) 1966-05-25 1966-05-25

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US (1) US3447339A (zh)
AT (1) AT271057B (zh)
BE (1) BE699019A (zh)
CH (1) CH472644A (zh)
DE (1) DE1551314A1 (zh)
ES (1) ES340878A1 (zh)
GB (1) GB1184364A (zh)
NL (1) NL6607168A (zh)
SE (1) SE306337B (zh)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3713305A (en) * 1968-06-05 1973-01-30 Philips Corp DEVICE FOR PRODUCING COLD AT TEMPERATURE LOWER THAN THAT OF lambda -POINT OF HELIUM
US3828564A (en) * 1970-02-27 1974-08-13 Linde Ag Closed refrigerant cycle for the liquefaction of low-boiling gases
US3910063A (en) * 1973-04-09 1975-10-07 Philips Corp Cooling system
US3932158A (en) * 1973-08-10 1976-01-13 Linde Aktiengesellschaft System for cooling an object with coolant cycle
US3978682A (en) * 1974-03-01 1976-09-07 U.S. Philips Corporation Refrigeration method and apparatus by converting 4 He to A superfluid
US4242885A (en) * 1977-12-23 1981-01-06 Sulzer Brothers Limited Apparatus for a refrigeration circuit
US4548053A (en) * 1984-06-05 1985-10-22 The United States Of America As Represented By The United States Department Of Energy Combined cold compressor/ejector helium refrigerator
US5347819A (en) * 1992-11-05 1994-09-20 Ishikawajima-Harima Heavy Industries, Co., Ltd. Method and apparatus for manufacturing superfluidity helium
US6438993B2 (en) * 2000-06-01 2002-08-27 Denso Corporation Ejector cycle system
US6477857B2 (en) * 2000-03-15 2002-11-12 Denso Corporation Ejector cycle system with critical refrigerant pressure
US20030131611A1 (en) * 2002-01-15 2003-07-17 Hiroshi Oshitani Air conditioner with ejector cycle system
US20050011221A1 (en) * 2003-07-18 2005-01-20 Tgk Co., Ltd. Refrigeration cycle
US20050061006A1 (en) * 2003-09-23 2005-03-24 Bonaquist Dante Patrick Biological refrigeration system
US20070000258A1 (en) * 2005-07-01 2007-01-04 Bonaquist Dante P Biological refrigeration sytem
US20130111935A1 (en) * 2010-07-23 2013-05-09 Carrier Corporation High Efficiency Ejector Cycle
US20140345318A1 (en) * 2011-11-17 2014-11-27 Denso Corporation Ejector-type refrigeration cycle device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3033238A1 (de) * 1980-09-04 1982-03-11 Mobil Oil Ag In Deutschland, 2000 Hamburg Verfahren und vorrichtung zur foerderung von raffineriegas in das heizgasnetz einer raffinerie

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3349161A (en) * 1964-12-30 1967-10-24 Avco Corp Electrical leads for cryogenic devices
US3360955A (en) * 1965-08-23 1968-01-02 Carroll E. Witter Helium fluid refrigerator
US3371145A (en) * 1968-02-27 Avco Corp Cryogenic heat exchanger electrical lead

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3371145A (en) * 1968-02-27 Avco Corp Cryogenic heat exchanger electrical lead
US3349161A (en) * 1964-12-30 1967-10-24 Avco Corp Electrical leads for cryogenic devices
US3360955A (en) * 1965-08-23 1968-01-02 Carroll E. Witter Helium fluid refrigerator

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3713305A (en) * 1968-06-05 1973-01-30 Philips Corp DEVICE FOR PRODUCING COLD AT TEMPERATURE LOWER THAN THAT OF lambda -POINT OF HELIUM
US3828564A (en) * 1970-02-27 1974-08-13 Linde Ag Closed refrigerant cycle for the liquefaction of low-boiling gases
US3910063A (en) * 1973-04-09 1975-10-07 Philips Corp Cooling system
US3932158A (en) * 1973-08-10 1976-01-13 Linde Aktiengesellschaft System for cooling an object with coolant cycle
US3978682A (en) * 1974-03-01 1976-09-07 U.S. Philips Corporation Refrigeration method and apparatus by converting 4 He to A superfluid
US4242885A (en) * 1977-12-23 1981-01-06 Sulzer Brothers Limited Apparatus for a refrigeration circuit
US4548053A (en) * 1984-06-05 1985-10-22 The United States Of America As Represented By The United States Department Of Energy Combined cold compressor/ejector helium refrigerator
US5347819A (en) * 1992-11-05 1994-09-20 Ishikawajima-Harima Heavy Industries, Co., Ltd. Method and apparatus for manufacturing superfluidity helium
US6574987B2 (en) * 2000-03-15 2003-06-10 Denso Corporation Ejector cycle system with critical refrigerant pressure
US6477857B2 (en) * 2000-03-15 2002-11-12 Denso Corporation Ejector cycle system with critical refrigerant pressure
US6438993B2 (en) * 2000-06-01 2002-08-27 Denso Corporation Ejector cycle system
US20030131611A1 (en) * 2002-01-15 2003-07-17 Hiroshi Oshitani Air conditioner with ejector cycle system
US6729157B2 (en) * 2002-01-15 2004-05-04 Denso Corporation Air conditioner with ejector cycle system
US20050011221A1 (en) * 2003-07-18 2005-01-20 Tgk Co., Ltd. Refrigeration cycle
US7207186B2 (en) * 2003-07-18 2007-04-24 Tgk Co., Ltd. Refrigeration cycle
US7059138B2 (en) * 2003-09-23 2006-06-13 Praxair Technology, Inc. Biological refrigeration system
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Also Published As

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AT271057B (de) 1969-05-27
DE1551314A1 (de) 1970-04-16
GB1184364A (en) 1970-03-18
NL6607168A (zh) 1967-11-27
BE699019A (zh) 1967-11-27
SE306337B (zh) 1968-11-25
ES340878A1 (es) 1968-06-16
CH472644A (de) 1969-05-15

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