US3473341A - Cold-gas refrigeration apparatus - Google Patents

Cold-gas refrigeration apparatus Download PDF

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Publication number
US3473341A
US3473341A US693943A US3473341DA US3473341A US 3473341 A US3473341 A US 3473341A US 693943 A US693943 A US 693943A US 3473341D A US3473341D A US 3473341DA US 3473341 A US3473341 A US 3473341A
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cold
ducts
space
heat
cooled
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US693943A
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English (en)
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Jan Mulder
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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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L59/00—Thermal insulation in general
    • F16L59/14—Arrangements for the insulation of pipes or pipe systems
    • F16L59/141—Arrangements for the insulation of pipes or pipe systems in which the temperature of the medium is below that of the ambient temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C3/00—Vessels not under pressure
    • F17C3/02—Vessels not under pressure with provision for thermal insulation
    • F17C3/08—Vessels not under pressure with provision for thermal insulation by vacuum spaces, e.g. Dewar flask
    • F17C3/085—Cryostats
    • 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
    • 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
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/42—Modularity, pre-fabrication of modules, assembling and erection, horizontal layout, i.e. plot plan, and vertical arrangement of parts of the cryogenic unit, e.g. of the cold box

Definitions

  • a refrigeration apparatus including a cold-gas refrigerator with its freezer as a source of cold gaseous medium 1 in combination with a cold-transport assembly for transporting the cold medium to an object to be cooled, the assembly including a vacuum-insulated housing about gastransporting ducts and gas-circulating means.
  • This invention relates to a device for cooling comprising a cold-gas refrigerator, having at least one compression space of variable volume in which a higher average temperature prevails during operation, and at least one expansion space likewise of variable volume in which a lower average temperature prevails during operation, these spaces being connected together and a regenerator being situated in said connection.
  • the device further comprises a cold transport device to transport cold supplied by the cold-gas refrigerator to the object to be cooled.
  • An object of the invention is to provide a device for cooling an object in which the cold-gas refrigerator and the object may be arranged at a distance from each other, and in which the cold from the cold-gas refrigerator is transported to the object to be cooled with a satisfactory thermal efiiciency at greatly divergent temperatures and over a long distance.
  • the device according to the invention is characterized in that the transport device is formed by a system of ducts which exchanges heat (a) with the space of the cold-gas refrigerator in which the lower average temperature prevails during operation, and (b) with the object to be cooled.
  • This system of ducts contains a gaseous medium under a pressure which is higher than the atmospheric pressure, and further a pumping device for circulating the medium by continuous displacement thereof.
  • the device according to the invention has the advantage that the ducts of the system may have a comparatively small diameter by using a gaseous medium under pressure in the system, whereby a sufiicient quantity of cold can be transported from the cold-gas refrigerator to the object to be cooled over a long distance with a relatively satisfactory thermal efiiciency.
  • a further advantage of the use of a gaseous medium is that cold can be transported at greatly divergent temperatures.
  • the density of the medium in the system of ducts will increase, particularly at low temperatures. Since the device according to the invention comprises a pump of the type by which the medium is displaced continuously, difiiculties caused by mass inertia forces which might indeed occur in pulsating pumping devices are not now experienced.
  • the medium is helium. This means that cold can be transported from the refrigerator to the object to be cooled throughout the range of temperatures above 4 K.
  • the pressure in the system of ducts is at least 10 atm. and at most atm. In this range of pressures the most advantageous thermal efliciencies are achieved with small diameters of ducts.
  • a further advantageous embodiment of the device according to the invention is characterized in that the system of ducts and selectively also the space of the coldgas refrigerator cooperating therewith and the object to be cooled are housed in a vacuum-insulated space in which at least part of the system of ducts, the space of the cold-gas refrigerator and the object to be cooled are surrounded by one or more radiation screens.
  • Each screen consists of one or more portions for shielding the relevant part of the system of ducts, refrigerator and object to be cooled from the wall of the vacuum space, each screen being in heat contact with a cold source which supplies cold at a higher temperature than that in the space of the cold-gas refrigerator which exchanges heat with the said system of ducts.
  • radiating heat is absorbed in a very advantageous manner by radiation screens surrounding the system of ducts, refrigerator and object to be cooled, said radiated heat being compensated for by cold from a cold source which supplies its cold at a higher temperature. Said cold supplied at a higher temperature can be produced at a higher efiiciency so that the total efficiency of the device is improved considerably. If, for example, the cold-gas refrigerator supplies its cold at approximately 20 K., the further cold source may be formed by a vessel containing liquid nitrogen, the radiating heat then being compensated for at the temperature of liquid nitrogen.
  • the radiation screens are in heat contact with the regenerator of the cold-gas refrigerator. Then the regeneration loss occurring in the regenerator is thus used at least in part for cooling the radiation screens, which results in an extremely simple device operating with very low losses.
  • the radiation screens are in heat contact with the expansion space of the higher average temperature while the system of ducts exchanges heat with the expansion space of the lower temperature on the one hand and with the object to be cooled on the other hand.
  • the heat contact between the radiation screens and the further cold source, regenerator and expansion space having a higher average temperature is formed by a second system of ducts which also contain a gaseous medium under pressure.
  • the radiation screens are secured in a heat conductive manner to the ducts of said second system of ducts, resulting in an extremely advantageous transport of cold from the further coldsource, the regenerator and the second expansion space to the radiation screens.
  • each system of ducts includes a pumping device formed by a housing which is divided in two parts by an insulating wall, the
  • first part housing an electric motor which is connected via a shaft passing with clearance through the partition to one or more fans present in the second part, the relevant system of ducts being connected to said second part.
  • the device is constructed in such manner that the same medium as in the system of ducts is present in the entire housing and that also the same pressure as in this system of ducts prevails in the entire housing. In this manner a very satisfactory seal of the system of ducts and the housing is achieved, and it has been found that the gaseous medium surrounding the electric motor has a sufliciently strong thermal conductivity to dissipate the heat of the electric motor.
  • the part of the housing accommodating the electric motor may then be arranged outside the vacuum-insulated space so that the heat of the electric motor is directly dissipated to the surroundings.
  • Another possibility is to arrange the electric motor also in the vacuum space, a part of the cold from the cold source then being used as cooling for the electric motor.
  • another embodiment of the invention has the part of the housing of the pumping device situated between the fans and the electric motor in heat contact with a cold source which supplies cold at a higher temperature than that at which the cold-gas refrigerator cooperating with the relevant system of ducts supplies its cold.
  • Said cold source may be the same as that with which the radiation screens are in heat contact, and in this manner heat leaking towards the system of ducts is again absorbed at an intermediate temperature level which is of course advantageous.
  • a pumping device is formed by a housing which is divided in three parts by two insulating walls.
  • the first part houses an electric motor Which is connected via a shaft passing with clearance through the two partitions to one or more fans rotatable Within the second part of the housing and to one or more fans rotatable within the third part of the housing.
  • the system of ducts is connected to the second part of the housing which is located between the electric motor and the third part of the housing, said system cooperating with the cold source, regenerator and an expansion space of the cold-gas refrigerator in which a higher average temperature prevails, while the system of ducts transporting cold from the space of the cold-gas refrigerator having the lowest average temperature to the object to be cooled is connected to the third part of the housing.
  • the electric motor of the pumping device is suitable to rotate at a high speed with the fan then having a small diameter and the connection shaft is then made of a poorly heat-conductive material.
  • the housing accommodating the electric motor and fans may also have a small diameter so that losses of cold through the wall of the housing will be small.
  • the electric motor and the bearing of the shaft may be at room temperature, the housing on the side of the fans being closed and on the side of the motor being provided with a cover which permits mounting or dismantling of the pump. In this manner a pump is obtained in which the seal and bearing are at room temperature which is very advantageous.
  • the object to be cooled is formed by at least part of a wall of a high-vacuum space which is surrounded by a further vacuum space in which a radiation screen surrounding the high-vacuum space is arranged, said radiation screen being in heat contact with the second system of ducts cooperating with the further cold source, regenerator and expansion space of higher average temperature.
  • FIGS. 1a and 1b show a cooling device comprising a cold-gas refrigerator and a system of ducts including a pumping device for transporting cold produced by the refrigerator to the object.
  • FIGURE 2 shows a device similar to that of FIGURE 1, but which comprises a second system of ducts including a pumping device, in which a medium circulates and which system exchanges heat with the regenerator of the cold-gas refrigerator, said system of ducts further being in heat contact with radiation screens, shielding the cold parts of the device from the wall of a vacuum space surrounding them.
  • a pumping device in which a medium circulates and which system exchanges heat with the regenerator of the cold-gas refrigerator, said system of ducts further being in heat contact with radiation screens, shielding the cold parts of the device from the wall of a vacuum space surrounding them.
  • FIGURE 3 shows a section of the device of FIGURE 2 taken on the line IIIII-I.
  • FIGURE 4 shows a device similar to that of FIGURE 2, which includes only one pumping device for circulating the medium in the two systems of ducts.
  • FIGURE 5 shows a device for cooling an object, comprising a multi-stage cold-gas refrigerator.
  • a cold-gas refrigerator 1 includes a piston 2 and a displacer 3.
  • the piston and displacer are connected to a driving mechanism (not shown) by a piston rod 4 and a displacer rod 5, respectively, the driving mechanism being able to move the piston and displacer with a mutual phase difference.
  • a driving mechanism not shown
  • the piston rod 4 and a displacer rod 5 respectively, the driving mechanism being able to move the piston and displacer with a mutual phase difference.
  • the device also includes a system of ducts 11 which on the one hand exchanges heat, at 12 with the freezer 10, and on the other hand exchanges heat, at 13, with the object 14 to be cooled, shown diagrammatically.
  • a pumping device 15 is included in the system of ducts 11 which contains gaseous helium under a pressure of 20 atm. circulated by the pumping device.
  • This pumping device consists of a housing 16 which is divided in two parts 18 and 19 by a partition 17.
  • the part 18 houses an electric motor 20 which is connected via a shaft 21 passing with clearance through the partition 17 to a fan 22 which is accommodated in the part 19.
  • the system of ducts 11 is connected to the part 19.
  • a Wall 23 surrounds those parts which will assume a low temperature during operation, it being possible to evacuate the space inside the wall 23.
  • the operation of said device is as follows: During operation the cold-gas refrigerator will produce cold in the expansion space 7, for example, at a temperature of 30 K.
  • the pumping device 15 circulates the helium which is present in the system of ducts 11 under a pressure of 20 atm. and is cooled in a heat exchanger 12 up to the temperature prevailing in the expansion space 7 after which it flows through the system of ducts 11 to the object 14 to be cooled where it absorbs heat in the heat exchanger 13, thus cooling the object 14.
  • the object 14 may be, for example, an electronic circuit, infrared equipment or a vacuum installation.
  • the electric motor including the bearing for the shaft 21 is always at room temperature which is advantageous especially for the bearing because ordinary ball-bearings can then be used.
  • the electric motor can rotate at a high speed so that the fan 22 may have a small diameter. This also results in a small diameter of the housing 16 so that the loss of cold through the wall will be limited.
  • the object 14 to be cooled may either be arranged outside the vacuum space 14A or inside it, and as is shown on an enlarged scale in FIGURE 1b it is also possible to incorporate the object 14 to be cooled together with the ducts exchanging heat therewith in a separate vacuum space 65.
  • the space 14A is then connected through a detachable connection sleeve 64 to the space 65.
  • the space 14A is closed by a cover 66.
  • the ducts of the system of ducts 11 then pass through this cover and are connected through the detachable connection sleeves 67 to the ducts exchanging heat with the object 14 to be cooled. In this manner the object to be cooled can easily be detached and replaced by another object to be cooled.
  • FIGURE 2 which shows a device similar to that of FIGURES 1
  • the parts which are at a low temperature are shielded from the cold wall 23 of the vacuum space by radiation screens.
  • the radiation screens are shown diagrammatically and indicated by the reference numerals 24.
  • the radiation screens 24 are in heat-conductive contact with a second system of ducts 25 which also contains helium under a pressure of 20 atm. and which includes a pumping device 26 of a construction similar to that of the pumping device 15 included in the system of ducts 11.
  • the system of ducts 25 exchanges heat with the regenerator 9, at 27. Consequently, the medium which is circulated in the system of ducts 25 will be cooled, at 27, after which said medium gives off its cold to the radiation screens 24 which are in heat-conductive contact with the system of ducts 25.
  • the system of ducts 11 (which exchanges heat with the freezer 10, at 12,) will have a temperature lower than that of the system of ducts 25 and the radiation screens 24 which are in heat-conductive contact therewith. This means that the system of ducts 11 and the object to be cooled are screened from the wall 23 of the vacuum space which will substantially be at room temperature, by radiation screens 24 of a higher temperature.
  • the heat radiating from the Wall 23 to the interior will be absorbed by the radiation screens 24, said radiated heat being compensated for by the cold which is derived from the regenerator, at 27.
  • the radiated heat is thus compensated for by at least part of the regeneration loss which normally occurs in the regenerator 9.
  • the efficiency of the cold-gas refrigerator is thus not decreased, while the efliciency of the entire device is improved because the radiated heat is compensated for at a higher temperature. In this manner a device is obtained with which the cold from the cold-gas refrigerator can be transported to the object to be cooled over a long distance and with very low loss.
  • the object to be cooled is formed by a high-vacuum space 70.
  • the system of ducts 11 is in heat contact with the wall of space 70 so that said wall will have substantially the temperature which prevails in expansion space 7.
  • This low temperature will reduce the vapour tension of gases in space 70 to a very low value so that a high vacuum can be created.
  • Surrounding the space 70 is a further vacuum space 71 in which a radiation screen 72 is arranged which is in heat contact with the system of ducts 25.
  • the coupling between the refrigerator including a cold transport device and the vacuum installation may again be constructed in the manner as shown in FIG- URE 1b.
  • FIGURE 4 shows a device which in broad outline corresponds to the device of FIGURE 2 but in which now only one pumping device 30 is present, which comprises a housing 31 subdivided in three parts 34, 35, and 36 by insulating partitions 32 and 33.
  • the electric motor 37 is arranged in the part 34 which motor is connected via shaft 38 passing with clearance through the partitions 32 and 33 to a fan 40 disposed in the part 35 and a fan 39 disposed in the part 36.
  • the system of ducts 11 is connected to the part 36 while the system of ducts 25 is connected to the part 35. In this manner not only a simple construction is obtained but also the part 36 which forms part of the system of ducts 25 containing the medium of a low temperature is again insulated from the electric motor 37.
  • FIGURE 5 shows a device similar to that of FIGURE 4 but in which now the coldgas refrigerator is designed as a two-stage cold-gas refrigerator.
  • Said cold-gas refrigerator comprises a piston 51 and a displacer consisting of two portions 52 and 53 of different diameters.
  • a compression space 54 is located above the piston 51 which space communicates with an intermediate expansion space 58 through a cooler 55, a first regenerator 56 and a first freezer 57.
  • the intermediate expansion space 58 communicates with the final expansion space 61 through a second regenerator 59 and a second freezer 60.
  • Said cold-gas refrigerator supplies cold in the expansion space 58 at a temperature of approximately 70 K., while cold is supplied in the extension space 61 at a temperature of approximately 20 K.
  • the system of ducts 11 exchanges heat, at 62, with the freezer 60, while the system of ducts 25 exchanges heat, at '63, with freezer 57.
  • the further operation and construction of this device is fully identical with that of the FIGURES 2 and 4.
  • the invention provides an extremely simple device for cooling an object in which the cold-gas refrigerator and the object are arranged at a distance from each other and with which cold can be transported over a long distance from the refrigerator to the object to be cooled with an extremely satisfactory thermal efficiency and at a very low temperature.
  • a refrigeration apparatus comprising a cold-gas refrigerator having at least one compression space and one expansion space connected through a regenerator, the spaces being of variable volume and operable at respectively higher and lower average temperatures, with the expansion space being a primary source of cold gaseous refrigerating medium, in combination with a cold-transport assembly including:
  • a primary device for circulating the medium through the duct system including (1) a pump for continuously displacing the medium with the pressure thereof being higher than atmospheric pressure through the duct system, (2) drive means for operating the pump; and (3) a casing having first and second parts and an insulating partition therebetween for enclosing the pump and drive means respectively,
  • a vacuum-insulated housing disposed about said first casing part including the pump and at least a major part of the duct system, providing space therein insulated from environmental heat, with the pumps drive means being disposed outside the vacuuminsulated housing and being operable at environmental temperature.
  • the compression space froms a second cold source having at temperature higher than the primary cold source, and at least one radiation screen disposed between at least parts of the primary duct system and an interior wall of the vacuum-insulated housing, the second cold source being connected to the screen for supplying cold thereto.
  • Apparatus as defined in claim 2 further comprising a second duct system extending between the second cold source and each screen, and a second device similar to the primary device for circulating the second medium through said second duct system.
  • first and second devices comprise first and second pumps and a single drive means for both pumps.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Health & Medical Sciences (AREA)
  • Clinical Laboratory Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
US693943A 1967-01-11 1967-12-27 Cold-gas refrigeration apparatus Expired - Lifetime US3473341A (en)

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NL6700375A NL6700375A (zh) 1967-01-11 1967-01-11

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US693943A Expired - Lifetime US3473341A (en) 1967-01-11 1967-12-27 Cold-gas refrigeration apparatus

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US (1) US3473341A (zh)
JP (1) JPS5113904B1 (zh)
BE (1) BE709262A (zh)
CH (1) CH477660A (zh)
FR (1) FR1561247A (zh)
GB (1) GB1213902A (zh)
NL (1) NL6700375A (zh)
SE (1) SE317986B (zh)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3600903A (en) * 1969-03-17 1971-08-24 Cryogenic Technology Inc Cryogenic heat station and apparatus incorporating the same
DE2349550A1 (de) * 1972-10-21 1974-05-02 Philips Nv Kaeltetransportleitung
EP0454491A2 (en) * 1990-04-26 1991-10-30 Forma Scientific, Inc. Laboratory freezer applicance
WO1997022839A1 (de) * 1995-12-15 1997-06-26 Leybold Vakuum Gmbh Tieftemperatur-refrigerator mit einem kaltkopf sowie verfahren zur optimierung des kaltkopfes für einen gewünschten temperaturbereich
EP0844446A1 (en) * 1996-11-15 1998-05-27 SANYO ELECTRIC Co., Ltd. Stirling refrigerating system
WO2001051863A1 (en) * 2000-01-11 2001-07-19 American Superconductor Corporation Cooling system for high temperature superconducting machines
US6597082B1 (en) 2000-08-04 2003-07-22 American Superconductor Corporation HTS superconducting rotating machine
EP1247325B2 (en) † 2000-01-11 2010-06-02 American Superconductor Corporation Hts superconducting rotating machine
US8955444B2 (en) 2012-07-31 2015-02-17 Electro-Motive Diesel, Inc. Energy recovery system for a mobile machine
US8960100B2 (en) 2012-07-31 2015-02-24 Electro-Motive Diesel, Inc. Energy recovery system for a mobile machine
US9073556B2 (en) 2012-07-31 2015-07-07 Electro-Motive Diesel, Inc. Fuel distribution system for multi-locomotive consist
US9718478B2 (en) 2012-07-31 2017-08-01 Electro-Motive Diesel, Inc. Fuel system for consist having daughter locomotive
CN117554155A (zh) * 2024-01-09 2024-02-13 北京飞斯科科技有限公司 一种用于电子自旋共振的顶部装卸型低温设备

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JP2016217616A (ja) * 2015-05-20 2016-12-22 株式会社 フジヒラ 極低温冷却装置

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US3101596A (en) * 1960-06-27 1963-08-27 Philips Corp Cold-gas refrigerator
US3260055A (en) * 1965-05-04 1966-07-12 James E Webb Automatic thermal switch
US3299646A (en) * 1964-06-17 1967-01-24 Little Inc A Cryogenic joule-thomson helium liquefier with cascade helium and nitrogen refrigeration circuits
US3368360A (en) * 1965-12-22 1968-02-13 Unicam Instr Ltd Cryogenic apparatus
US3383871A (en) * 1965-10-09 1968-05-21 Philips Corp Apparatus for transporting cold to a remote location using an expansion ejector
US3396547A (en) * 1965-10-09 1968-08-13 Philips Corp Cold transport to a remote location with small temperature drop

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3101596A (en) * 1960-06-27 1963-08-27 Philips Corp Cold-gas refrigerator
US3299646A (en) * 1964-06-17 1967-01-24 Little Inc A Cryogenic joule-thomson helium liquefier with cascade helium and nitrogen refrigeration circuits
US3260055A (en) * 1965-05-04 1966-07-12 James E Webb Automatic thermal switch
US3383871A (en) * 1965-10-09 1968-05-21 Philips Corp Apparatus for transporting cold to a remote location using an expansion ejector
US3396547A (en) * 1965-10-09 1968-08-13 Philips Corp Cold transport to a remote location with small temperature drop
US3368360A (en) * 1965-12-22 1968-02-13 Unicam Instr Ltd Cryogenic apparatus

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3600903A (en) * 1969-03-17 1971-08-24 Cryogenic Technology Inc Cryogenic heat station and apparatus incorporating the same
DE2349550A1 (de) * 1972-10-21 1974-05-02 Philips Nv Kaeltetransportleitung
EP0454491A2 (en) * 1990-04-26 1991-10-30 Forma Scientific, Inc. Laboratory freezer applicance
EP0454491A3 (en) * 1990-04-26 1992-03-11 Forma Scientific, Inc. Laboratory freezer applicance
WO1997022839A1 (de) * 1995-12-15 1997-06-26 Leybold Vakuum Gmbh Tieftemperatur-refrigerator mit einem kaltkopf sowie verfahren zur optimierung des kaltkopfes für einen gewünschten temperaturbereich
US6065295A (en) * 1995-12-15 2000-05-23 Leybold Vakuum Gmbh Low-temperature refrigerator with cold head and a process for optimizing said cold head for a desired temperature range
EP0844446A1 (en) * 1996-11-15 1998-05-27 SANYO ELECTRIC Co., Ltd. Stirling refrigerating system
AU732327B2 (en) * 1996-11-15 2001-04-12 Sanyo Electric Co., Ltd. Stirling refrigerating system
WO2001051863A1 (en) * 2000-01-11 2001-07-19 American Superconductor Corporation Cooling system for high temperature superconducting machines
US6347522B1 (en) 2000-01-11 2002-02-19 American Superconductor Corporation Cooling system for HTS machines
US6625992B2 (en) 2000-01-11 2003-09-30 American Superconductor Corporation Cooling system for HTS machines
EP1247325B2 (en) † 2000-01-11 2010-06-02 American Superconductor Corporation Hts superconducting rotating machine
US6597082B1 (en) 2000-08-04 2003-07-22 American Superconductor Corporation HTS superconducting rotating machine
US8955444B2 (en) 2012-07-31 2015-02-17 Electro-Motive Diesel, Inc. Energy recovery system for a mobile machine
US8960100B2 (en) 2012-07-31 2015-02-24 Electro-Motive Diesel, Inc. Energy recovery system for a mobile machine
US9073556B2 (en) 2012-07-31 2015-07-07 Electro-Motive Diesel, Inc. Fuel distribution system for multi-locomotive consist
US9718478B2 (en) 2012-07-31 2017-08-01 Electro-Motive Diesel, Inc. Fuel system for consist having daughter locomotive
CN117554155A (zh) * 2024-01-09 2024-02-13 北京飞斯科科技有限公司 一种用于电子自旋共振的顶部装卸型低温设备
CN117554155B (zh) * 2024-01-09 2024-03-29 北京飞斯科科技有限公司 一种用于电子自旋共振的顶部装卸型低温设备

Also Published As

Publication number Publication date
FR1561247A (zh) 1969-03-28
SE317986B (zh) 1969-12-01
JPS5113904B1 (zh) 1976-05-04
BE709262A (zh) 1968-07-11
NL6700375A (zh) 1968-07-12
CH477660A (de) 1969-08-31
GB1213902A (en) 1970-11-25

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