US2906101A - Fluid expansion refrigeration method and apparatus - Google Patents

Fluid expansion refrigeration method and apparatus Download PDF

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Publication number
US2906101A
US2906101A US696506A US69650657A US2906101A US 2906101 A US2906101 A US 2906101A US 696506 A US696506 A US 696506A US 69650657 A US69650657 A US 69650657A US 2906101 A US2906101 A US 2906101A
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United States
Prior art keywords
fluid
chamber
chambers
conduit
piston
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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.)
Expired - Lifetime
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US696506A
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English (en)
Inventor
Howard O Mcmahon
William E Gifford
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Arthur D Little Inc
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Arthur D Little Inc
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
Priority to NL233237D priority Critical patent/NL233237A/xx
Priority to NL113898D priority patent/NL113898C/xx
Priority to NL252718D priority patent/NL252718A/xx
Application filed by Arthur D Little Inc filed Critical Arthur D Little Inc
Priority to US696506A priority patent/US2906101A/en
Priority to GB35995/58A priority patent/GB882656A/en
Priority to FR779038A priority patent/FR1215279A/fr
Priority to DEL31719A priority patent/DE1282661B/de
Priority claimed from US820671A external-priority patent/US2966034A/en
Priority to US831596A priority patent/US2966035A/en
Priority to CH7740459A priority patent/CH376945A/de
Publication of US2906101A publication Critical patent/US2906101A/en
Application granted granted Critical
Priority to DE19601401515 priority patent/DE1401515A1/de
Priority to CH682960A priority patent/CH391754A/de
Priority to GB20992/60A priority patent/GB938182A/en
Priority to FR830084A priority patent/FR78069E/fr
Priority to SE5853/60A priority patent/SE304526B/xx
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/004—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2242/00—Ericsson-type engines having open regenerative cycles controlled by valves
    • F02G2242/40—Piston-type engines
    • F02G2242/42—Piston-type engines having a single piston regenerative displacer attached to the piston, e.g. "Gifford-McMahon" engines

Definitions

  • This invention relates to refrigeration methods and apparatus for the production of low temperatures and liquefied gases at low temperatures.
  • One well known form of refrigeration apparatus comprises a cylinder having relatively Warm and cold ends interconnected through a cooler and a regenerator, 'respectively for removing heat of compression and for storing heat. Movement of a piston-like displacer within the cylinder causes the working fluid to flow in either of two directions through the regenerator. A separate piston, also within the cylinder, alternately compresses and expands the volume of fluid in the chambers in coordination with the displacer.
  • the displacer and piston are separately driven, usually by cams, such that the fluid volume is compressed after the displacer has moved it to the warm end; the displacer then moves the fluid to the cold end through the cooler which removes heat of compression and through the regenerator which further cools the fluid; and the piston then allows the cooled fluid to expand in volume and thereby further cool itself and the surrounding cylinder.
  • the refrigeration so produced may be extracted by heat exchange with the cooled cylinder or fluid.
  • One object of the present invention is to provide a novel method of fluid refrigeration which eliminates the need for close cooperation between the cyclic fluid compression and expansion of prior methods and which more efficiently utilizes expansion cooling of a refrigeration fluid.
  • a fluid refrigeration method comprises continuously compressing a fluid, removing heat of compression and storing the compressed fluid, connect- H shown partly in section.
  • Further objects of the invention are to provide novel apparatus for carrying out a refrigeration process which avoids operation of valves at low temperatures, which eliminates complicated mechanism for coordinating pistons and displacers, and which is adapted for multi-stage refrigeration while avoiding the use of pressure seals at low temperatures.
  • refrigeration apparatus comprises an enclosure, movable means forming with the enclosure an expansible chamber, valve means external of the enclosure for admitting compressed fluid to and releasing fluid from said chamber, and a conduit including thermal storage means between said chamber and said valve means thermally isolating said valve means from said chamber, said fluid undergoing expansion and cooling in said chamber, and said movable means causing exhaust of said cooled gas through said conduit.
  • movable means such as a piston which includes a plurality of sections respectively forming with the enclosure a plurality of concomitantly expansible chambers, with at least one thermal storage means connected between said respective chambers.
  • Fig. 5 is a diagrammatic view of a refrigeration system
  • Figs. 1 to 4 is illustrated schematically the operating cycle of the present refrigeration process.
  • a refrigerating fluid such as helium
  • a compressor C storage device 30 such as a regenerator.
  • the first step is the supply of the continuously compressed and. cooled fluid to the chamber *9, (see Fig. 2) now substantially filled by the piston 2.
  • the fluid is partially cooled by the regenerator 30 whose temperature is reduced as will hereafter be explained.
  • the compressed fluid is then taken into the chamber (Fig. 2).-
  • the supply of fluid is then discontinued by closing valve- V1, and the partially cooled fluid expands and cools itself and the chamber 9 in a well-known manner-during further movement of the piston (Fig. 3a) mechanical energy being expended in such movement of the piston;
  • multi-stage refrigeration apparatus coniprises a cylinder 1 in which are fitted piston sections 2, 3 and 4.
  • the piston sections are connected mechanically by linear springs 7 and 8, and a spring 6 is disposed between piston section 2 and the cylinder end wall 1a so as to divide the cylinder into three chambers 9, 1t ⁇ and 11.
  • a piston rod '12 driven through a connecting pin 14 by a flywheel 13, reciprocates the uppermost piston section 4 from a down position, through the position shown, to an up position. Sealing rings 5, and if necessary, oil lubrication on the periphery of section 4, seal the chamber 11.
  • the top piston section 4 When the flywheel pin 14 coupled to the rod 12 is in its lowest position I, the top piston section 4 is in a position in which it abuts the intermediate cylinder 3, filling the intermediate space 11.
  • the connecting springs 8 and 7 respectively hold the lower pistons 3 and 2 downwardly against the spring 6, so that adjacent piston sections abut each other and the lower piston 2 abuts the end wall 1a of the cylinder.
  • the chambers 9, and 11 are filled by the piston sections.
  • the springs 6, 7 and 8 are formed with a rectangular cross-section, and when fully compressed fill annular recesses 16 in opposed piston faces and the cylinder end wall 5.
  • the relative lengths of the springs between the piston faces, or their stiffness, are selected such that the three chambers are progressively larger in volume in the order 9, 10 and 11.
  • a temperature diflerential exists between the chambers, chamber 9 being the coldest, chamber 10 being warmer and chamber 11 the warmest.
  • their relative volumes will depend on the lowest temperatures at which it is desired to operate the engine. It may be desirable to open the lower chamber 9 in advance of opening chambers 10 and 11, in which case the lowest spring 6 would be selected to cause sections 3 and 4 to follow section 2 during the early part of its stroke.
  • another chamber may be caused to open first, or all three chambers may be caused to open simultaneously.
  • ports 17, 18 and 19 Communicating with the chambers 9, 10 and 11 respectively are ports 17, 18 and 19 which include narrow, shallow channels in the inner cylinder wall. Connecting the ports are conduits 21, 22 and 23 which pass through thermal storage means 24 and 25 such as regenerators.
  • Thermal transfer means 20 such as a heat exchanger having a. secondary input 27 and output 28 for a refrigerating medium is connected between the chamber 9 and regenerator 24. From conduit 23 a supply conduit 29 is connected through a regenerator 30 to valves V1 and V2. It will be understood that, although omitted for the purpose of clearer illustration, insulation is provided around the cylinder 1, the regenerators 24, 25 and 30 and the heat exchanger 20.
  • Valve V2 is connected to a low pressure ballast tank LP which is exhausted by a compressor C.
  • the compressor C pumps a refrigeration fluid through a water cooled heat exchanger A, for example, and thence through a cleaning device B for removing oil vapor, to a high pres- 4 sure ballast tank HP.
  • Valve V1 when open supplies compressed fluid from the high pressure ballast HP to the supply conduit 29.
  • a flask F supplies fluid to the system through a check valve as needed.
  • valves V1 and V2 are accomplished by earns 31 and 32, respectively operating through follower rods 33 and 34 pivotally connected to valve levers 35 and 36.
  • the valve cams are driven through a connection 37 in synchronism with the flywheel 13.
  • one valve performing the function of the two valves shown may be substituted for the two valves shown.
  • flywheel position I the chambers 9 to 11 are substantially filled by the piston sections and exhausted of fluid. Both valves V1 and V2 are closed. Clockwise rotation of the flywheel toward position II opens valve V1 admitting fluid under pressure and at reference temperature, 300 K. for example, to the supply conduit 29. Concomitantly, that is, during overlapping periods, the piston sections begin an expansion stroke expanding the inter-piston chambers. Expansion of the chambers draws fluid through the thermal storage means 30, 25 and 24 to the chambers.
  • the upper storage means 30 acts as a precooler for the middle storage means 25, and the middle a precooler for the lower means 24, the several storage means are at progressively lower temperatures descending in the order 30, 25 and 24, so that fluid entering chamber 9 will be colder than that entering chamber 10, which in turn is colder than that entering chamber 11. Valve V1 remaining open, the pressure remains high despite cooling of the fluid during intake.
  • valve V1 is closed, and the continuing expansion stroke isentropically expands the fluid in all three chambers. Since the fluid is at high pressure, as described above, it moves the piston upward in the manner described with reference to Fig. 3a, and thereby delivers mechanical work externally of the cylinder 1, which work is delivered to the flywheel 13 and absorbed by a brake 15 (Fig. 5).
  • the fluid in each chamber is cooled, according to well-known principles, below its starting temperature just prior to expansion. Since the several starting temperatures are progressively lower in chambers 11, 10 and 9 respectively, their final temperatures will be progressively lower, that in chamber 9 being the lowest. The walls of the chambers will simultaneously be cooled by the fluid toward the same temperatures.
  • valve V2 is opened, connecting the chambers with the low pressure ballast LP.
  • the fluid in the chambers may then further expand and cool during exhaust through the thermal transfer means 24, 25 and 30, but preferably the latter part of the expansion stroke of the piston sections reduces the fluid pressure to that of the low pressure ballast LP.
  • valve V2 remains open and V1 closed, and during the accompanying compression stroke the piston sections fill the chambers and exhaust the cooled fluid through the several storage means. Since the low pressure ballast LP may be at the same pressure as the expanded fluid in the chambers, no external work need be expended on the flywheel during the herein-called compression stroke.
  • conduits and thermal storage means are shown connected externally of the cylinder, other forms of conduits and storage means may be employed. And, although low and high pressure ballasts connected to the chambers by separate valve means are shown, various other fluid supplies may be used.
  • a multistage, fluid refrigeration system comprising a low pressure ballast, a compressor, a thermal exchange cooler and a high pressure ballast connected in series to provide in said high pressure ballast a continuous supply of compressed fluid at approximately ambient reference temperature, a cylinder, a plurality of spring coupled piston sections reciprocable in said cylinder and forming therewith a plurality of spaced chambers, a single piston drive means extending externally of the cylinder and connected to one piston section for causing said sections concomitantly to expand and compress said chambers, valve means external of the cylinder for supplying compressed fluid to and releasing fluid from said chambers, conduit means connecting said valve means to one of said chambers at one end of the cylinder including thermal storage means thermally isolating said valve means from said one end, said chambers decreasing in relative volume in a direction away from said valve means, additional conduit means, including thermal storage means, between each of said chambers, and means for coordinating actuation of said drive means and valve means such that said valve means supplies compressed fluid from said high pressure ballast to said chamber through
  • the fluid refrigeration method which comprises supplying an initial quantity of refrigeration fluid at a given temperature and under high pressure along a path to an enclosed space, removing and storing heat from the fluid during supply along said path thereby initially cooling the fluid, continuing supply of high pressure fluid throughout said initial cooling thereby to maintain said high pressure by addition of fluid until a final quantity of cooled fluid under said high pressure is supplied to said space, discontinuing supply of high pressure fluid, eflecting expansion of said final quantity of fluid by delivery of energy external of said space thereby further to cool and extract energy from the fluid in said space, and exhausting the further cooled fluid from said space through said path, the further cooled fluid receiving heat previously stored along said path.
  • the fluid refrigeration method which comprises supplying an initial quantity of refrigeration fluid at a given temperature and under high pressure along a path to an enclosed space, removing and storing heat from the fluid during supply along said path thereby initially cooling the fluid, continuing supply of high pressure fluid throughout said initial cooling thereby to maintain said high pressure by addition of fluid until a final quantity of cooled fluid under said high pressure is supplied to said space, discontinuing supply of high pressure fluid, effecting expansion of said final quantity of fluid by delivery of mechanicalwork external of said space thereby further to cool and extract energy from the fluid in said space, and exhausting the further cooled fluid from said space through said path, the further cooled fluid receiving heat previously stored along said path.
  • the fluid refrigeration method which comprises supplying an initial quantity of refrigeration fluid at a given temperature and under high pressure along a path to an enclosed space, removing and storing heat from the fluid during supply along said path thereby initially cooling the fluid, continuing supply of high pressure fluid throughout said initial cooling thereby to maintain said high pressure by addition of fluid until a final quantity of cooled fluid under said high pressure is supplied to said space, discontinuing supply of high pressure fluid, effecting expansion of said final quantity of fluid by delivery of energy external of said space thereby further to cool and extract energy from the fluid in said space, and exhausting the further cooled fluid from said space through said path, the further cooled fluid delivering refrigeration to a thermal load in said path and then receiving heat previously stored along said path.
  • the fluid refrigeration method which comprises supplying an initial quantity of refrigeration fluid at a given temperature and under high pressure along a path to an enclosed space, removing and storing heat from the fluid during supply along said path thereby initially cooling the fluid, the heat being stored at continually lower temperatures along the path, continuing supply of high pressure fluid throughout said initial cooling thereby to maintain said high pressure by addition of fluid until a final quantity of cooled fluid under said high pressure is supplied to said space, discontinuing supply of high pressure fluid, effecting expansion of said final quantity of fluid by delivery of energy external of said space thereby further to cool and extract energy from the fluid in said space, and exhausting the further cooled fluid from said space through said path, the further cooled fluid receiving heat previously stored along said path.
  • Fluid expansion refrigeration apparatus comprising a fluid transfersystem including an enclosure, movable means forming With'the enclosure an expansible chamber, and a conduit including thermal storage means connected to said chamber; valve means connected to said conduit for admitting compressed fluid to and releasing fluid from the chamber, control means coordinating said movable means and valve means to supply a quantity of compressed fluid to said conduit while said movable means causes said chamber to expand, said control means being timed thereafter to cause one of said movable means and valve means to release pressure on the quantity of fluid in said chamber thereby to effect expansion and cooling of said quantity of fluid by delivery of energy externally of said system.
  • Fluid expansion refrigeration apparatus comprising a fluid transfer system including an enclosure, movable means forming with the enclosure an expansible chamber, and a conduit including thermal storage means connected to said chamber; valve means connected to said conduit for admitting compressed fluid to and releasing fluid from the chamber through said conduit, said thermal storage means being adapted to progressively cool said fluid during admission therethrough, control means coordinating said movable means and valve means to supply a quantity of compressed fluid to said conduit while said movable means causes said chamber to expand, said control means being timed thereafter to cause one of said movable means and valve means to release pressure on the quantity of fluid in said chamber thereby to effect expansion and cooling of said quantity of fluid by delivery of energy externally of said system.
  • Fluid expansion refrigeration apparatus comprising a fluid transfer system including an enclosure, movable means forming with the enclosure an expansible chamber, and a conduit including thermal storage means connected to said chamber; valve means connected to said conduit for admitting compressed fluid to and releasing fluid from the chamber through said conduit, said thermal storage means being adapted to progressively cool said fluid during admission therethrough, control means coordinating said movable means and valve means to supply an initial quantity of compressed fluid to said conduit and continue said supply while said movable means causes said chamber to expand, and take in a final quantity of cooled compressed gas, said control means being timed thereafter to cause one of said movable means and valve means to release pressure on the quantity of fluid in said chamber thereby to effect expansion and cooling of said quantity of fluid by delivery of energy externally of said system.
  • Fluid expansion refrigeration apparatus comprising a fluid transfer system including an enclosure, movable means forming with the enclosure an expansible chamber, and a conduit including thermal storage means connected to said chamber; valve means connected to said conduit for admitting compressed fluid to and releasing fluid from the chamber, control means coordinating said movable means and valve means to supply a quantity of compressed fluid to said conduit while said movable means causes said chamber to expand, said control means being timed thereafter to cause one of said movable means and valve means to release pressure on the quantity of fluid in said chamber thereby to effect expansion and cooling of said quantity of fluid by delivery of energy externally of said system, and means external of the system for absorbing said energy.
  • Fluid expansion refrigeration apparatus comprising a fluid transfer system including an enclosure, movable means forming with the enclosure an expansible chamber, and a conduit including thermal storage means connected to said chamber; valve means connected to said conduit for admitting compressed fluid to and releasing fluid from the chamber, control means coordinating said movable means and valve means to supply a quantity of compressed fluid to said conduit while said movable means causes said chamber to expand, said con- '8 trolmeans being timed thereafter to cause said movable means to release pressure on the quantity of fluid in said chamber thereby to effect expansion and cooling of said quantity of fluid by motion of said movable means, and work absorbing means mechanically connected to said movable means for absorbing the energy of said motion.
  • Fluid expansion refrigeration apparatus comprising a fluid transfer system including an enclosure, movable means forming with the enclosure a plurality of expansible chambers, and a conduit including thermal storage means connected to respective chambers; valve means connected to said conduit for admitting compressed fluid to and releasing fluid from said chambers, control means coordinating said movable means and valve means to supply a quantity of compressed fluid to said conduit while said movable means causes said chambers to expand, said control means being timed thereafter to cause one of said movable means and valve means to release pressure on the quantity of fluid in said chambers thereby to effect expansion and cooling of said quantity of fluid by delivery of energy externally of said system.
  • Fluid expansion refrigeration apparatus comprising a fluid transfer system including an enclosure, a plurality of movable means forming with the enclosure a plurality of expansible chambers, and a conduit including a plurality of thermal storage means respectively connected to said chambers; valve means connected to said conduit for admitting compressed fluid to and releasing fluid from said chambers, control means coordinating said movable means and valve means to supply a quantity of compressed lluid to said conduit while said movable means causes said chambers to expand, said control means being timed thereafter to cause one of said movable means and valve means to release pressure on the quantity of fluid in said chambers thereby to effect expansion and cooling of said quantity of fluid by delivery of energy externally of said system.
  • Fluid expansion refrigeration apparatus comprising a fluid transfer system including an enclosure, movable means forming with the enclosure a plurality of expansible chambers, and a conduit including thermal storage means connected to respective chambers; valve means connectcd to said conduit for admitting compressed fluid to and releasing fluid from said chambers, control means coordinating said movable means and valve means to supply a quantity of compressed fluid to said conduit while said movable means causes said chambers to expand, said control means being timed thereafter to cause one of said movable means and valve means to release pressure on the quantity of fluid in said chambers thereby to effect expansion and cooling of said quantity of fluid by delivcry of energy externally of said system, and means external of the system for absorbing said energy.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Confectionery (AREA)
US696506A 1957-11-14 1957-11-14 Fluid expansion refrigeration method and apparatus Expired - Lifetime US2906101A (en)

Priority Applications (14)

Application Number Priority Date Filing Date Title
NL233237D NL233237A (fr) 1957-11-14
NL113898D NL113898C (fr) 1957-11-14
NL252718D NL252718A (fr) 1957-11-14
US696506A US2906101A (en) 1957-11-14 1957-11-14 Fluid expansion refrigeration method and apparatus
GB35995/58A GB882656A (en) 1957-11-14 1958-11-10 Improvements in or relating to methods of and apparatus for refrigeration
FR779038A FR1215279A (fr) 1957-11-14 1958-11-13 Procédé et appareil de réfrigération
DEL31719A DE1282661B (de) 1957-11-14 1958-11-14 Vorrichtung zur Kaelteerzeugung
US831596A US2966035A (en) 1957-11-14 1959-08-04 Refrigeration method and apparatus
CH7740459A CH376945A (de) 1957-11-14 1959-08-26 Verfahren und Einrichtung zur Expansion eines gasförmigen Mediums
DE19601401515 DE1401515A1 (de) 1957-11-14 1960-06-14 Verfahren und Geraet zur Kaelteerzeugung unter Entspannung eines Kaeltemittels
CH682960A CH391754A (de) 1957-11-14 1960-06-15 Verfahren zur Expansion eines gasförmigen Mediums und Einrichtung zur Durchführung des Verfahrens
GB20992/60A GB938182A (en) 1957-11-14 1960-06-15 Fluid expansion refrigeration method and apparatus
FR830084A FR78069E (fr) 1957-11-14 1960-06-15 Procédé et appareil de réfrigération
SE5853/60A SE304526B (fr) 1957-11-14 1960-06-15

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US696506A US2906101A (en) 1957-11-14 1957-11-14 Fluid expansion refrigeration method and apparatus
US820671A US2966034A (en) 1959-06-16 1959-06-16 Reciprocating flow gas expansion refrigeration apparatus and device embodying same
US831596A US2966035A (en) 1957-11-14 1959-08-04 Refrigeration method and apparatus

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Publication Number Publication Date
US2906101A true US2906101A (en) 1959-09-29

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US696506A Expired - Lifetime US2906101A (en) 1957-11-14 1957-11-14 Fluid expansion refrigeration method and apparatus
US831596A Expired - Lifetime US2966035A (en) 1957-11-14 1959-08-04 Refrigeration method and apparatus

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Application Number Title Priority Date Filing Date
US831596A Expired - Lifetime US2966035A (en) 1957-11-14 1959-08-04 Refrigeration method and apparatus

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US (2) US2906101A (fr)
DE (2) DE1282661B (fr)
FR (1) FR1215279A (fr)
GB (2) GB882656A (fr)
NL (3) NL233237A (fr)
SE (1) SE304526B (fr)

Cited By (42)

* Cited by examiner, † Cited by third party
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US2966035A (en) * 1957-11-14 1960-12-27 Little Inc A Refrigeration method and apparatus
US3214924A (en) * 1962-07-26 1965-11-02 Philips Corp Method of absorbing thermal energy at low temperatures and apparatus for carrying out such methods
US3218815A (en) * 1964-06-17 1965-11-23 Little Inc A Cryogenic refrigeration apparatus operating on an expansible fluid and embodying a regenerator
US3221509A (en) * 1964-01-16 1965-12-07 Ibm Refrigeration method and apparatus
US3274795A (en) * 1964-04-30 1966-09-27 Little Inc A Fluid operating apparatus
US3274786A (en) * 1964-07-27 1966-09-27 Little Inc A Cryogenic refrigeration method and apparatus operating on an expansible fluid
US3362174A (en) * 1963-10-14 1968-01-09 Air Liquide Gaseous condensation in vacuum with plural refrigerants
DE2051203A1 (de) * 1969-10-20 1971-05-06 Air Products and Chemicals Ine, Philadelphia, Pa (V St A ) Verfahren und Vorrichtung zur Kalte erzeugung mittels eines Kuhlmittels
US3692099A (en) * 1968-06-20 1972-09-19 Gen Electric Ultra low temperature thermal regenerator
US3913339A (en) * 1974-03-04 1975-10-21 Hughes Aircraft Co Reduction in cooldown time for cryogenic refrigerator
US4294600A (en) * 1979-10-29 1981-10-13 Oerlikon-Buhrle U.S.A. Inc. Valves for cryogenic refrigerators
US4294077A (en) * 1979-10-29 1981-10-13 Oerlikon-Buhrle U.S.A. Inc. Cryogenic refrigerator with dual control valves
US4305741A (en) * 1979-10-29 1981-12-15 Oerlikon-Buhrle U.S.A. Inc. Cryogenic apparatus
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US4333755A (en) * 1979-10-29 1982-06-08 Oerlikon-Buhrle U.S.A. Inc. Cryogenic apparatus
DE3044427A1 (de) * 1980-11-26 1982-06-24 Leybold-Heraeus GmbH, 5000 Köln Verdraenger fuer refrigeratoren
US4339927A (en) * 1981-07-06 1982-07-20 Oerlikon-Burhle U.S.A. Inc. Gas-driven fluid flow control valve and cryopump incorporating the same
US4372128A (en) * 1981-11-02 1983-02-08 Oerlikon-Buhrle U.S.A. Inc. In-line cryogenic refrigeration apparatus operating on the Stirling cycle
DE3201496A1 (de) * 1982-01-20 1983-07-28 Leybold-Heraeus GmbH, 5000 Köln Refrigerator
US4490983A (en) * 1983-09-29 1985-01-01 Cryomech Inc. Regenerator apparatus for use in a cryogenic refrigerator
EP0160808B1 (fr) * 1984-04-11 1988-04-27 Leybold Aktiengesellschaft Machine frigorifique
US4767123A (en) * 1985-09-02 1988-08-30 Leybold-Heraeus Gmbh Dual ring piston-ring system with spring ring bias means
US4793153A (en) * 1987-06-12 1988-12-27 Recovery Engineering, Inc. Energy recovery apparatus
US4848092A (en) * 1987-10-02 1989-07-18 Gifford Peter E Heat exchanger for cryogenic refrigerator
JPH03105166A (ja) * 1989-09-20 1991-05-01 Toshiba Corp 極低温冷凍機
US5113663A (en) * 1991-03-11 1992-05-19 Cryomech, Inc. Multi-stage cryogenic refrigerator
US5590534A (en) * 1994-08-01 1997-01-07 Hollandse Signaalapparaten B.V. Stirling cooler
US5735127A (en) * 1995-06-28 1998-04-07 Wisconsin Alumni Research Foundation Cryogenic cooling apparatus with voltage isolation
US6256997B1 (en) 2000-02-15 2001-07-10 Intermagnetics General Corporation Reduced vibration cooling device having pneumatically-driven GM type displacer
EP1192393A2 (fr) * 1999-07-06 2002-04-03 Massachusetts Institute Of Technology Cryorefrigerateur modulaire a haut rendement pourvu d'un detendeur a piston flottant
WO2004003442A1 (fr) 2002-06-29 2004-01-08 Leybold Vakuum Gmbh Refrigerateur pourvu d'un regenerateur
US20040066811A1 (en) * 2002-07-15 2004-04-08 Cyber Laser Inc. Helium-cooled laser device
US20070253854A1 (en) * 2006-04-28 2007-11-01 Stephen Dunn Compressor with oil bypass
US20070261418A1 (en) * 2006-05-12 2007-11-15 Flir Systems Inc. Miniaturized gas refrigeration device with two or more thermal regenerator sections
WO2009146120A1 (fr) 2008-04-04 2009-12-03 Brooks Automation, Inc. Pompe cryogénique employant des alliages étain-antimoine et procédés d’utilisation
US20110107790A1 (en) * 2009-11-09 2011-05-12 Stephen Dunn Air Cooled Helium Compressor
US8187370B2 (en) 2006-07-13 2012-05-29 Shi-Apd Cryogenics, Inc. Horizontal bulk oil separator
US10240832B2 (en) 2015-12-18 2019-03-26 Sumitomo (Shi) Cryogenic Of America, Inc Helium compressor with dual after-coolers
DE112005003132B4 (de) 2005-01-13 2019-08-08 Sumitomo Heavy Industries, Ltd. Kroygener Kühler mit verringerter Eingangsleistung
WO2019199591A1 (fr) 2018-04-09 2019-10-17 Brooks Automation, Inc. Refroidisseur cryogénique à entraînement pneumatique
US11149992B2 (en) 2015-12-18 2021-10-19 Sumitomo (Shi) Cryogenic Of America, Inc. Dual helium compressors
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EP0160808B1 (fr) * 1984-04-11 1988-04-27 Leybold Aktiengesellschaft Machine frigorifique
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EP1192393A2 (fr) * 1999-07-06 2002-04-03 Massachusetts Institute Of Technology Cryorefrigerateur modulaire a haut rendement pourvu d'un detendeur a piston flottant
US6256997B1 (en) 2000-02-15 2001-07-10 Intermagnetics General Corporation Reduced vibration cooling device having pneumatically-driven GM type displacer
DE10190484B3 (de) 2000-02-15 2018-07-12 Intermagnetics General Corp. Expander des gm-typs zur verwendung in einem kryogenen kühlsystem
WO2004003442A1 (fr) 2002-06-29 2004-01-08 Leybold Vakuum Gmbh Refrigerateur pourvu d'un regenerateur
US7123635B2 (en) * 2002-07-15 2006-10-17 Cyber Laser Inc. Helium-cooled laser device
US20040066811A1 (en) * 2002-07-15 2004-04-08 Cyber Laser Inc. Helium-cooled laser device
DE112005003132B4 (de) 2005-01-13 2019-08-08 Sumitomo Heavy Industries, Ltd. Kroygener Kühler mit verringerter Eingangsleistung
US20070253854A1 (en) * 2006-04-28 2007-11-01 Stephen Dunn Compressor with oil bypass
US7674099B2 (en) 2006-04-28 2010-03-09 Sumitomo Heavy Industries, Ltd. Compressor with oil bypass
US8959929B2 (en) * 2006-05-12 2015-02-24 Flir Systems Inc. Miniaturized gas refrigeration device with two or more thermal regenerator sections
US20070261418A1 (en) * 2006-05-12 2007-11-15 Flir Systems Inc. Miniaturized gas refrigeration device with two or more thermal regenerator sections
US8187370B2 (en) 2006-07-13 2012-05-29 Shi-Apd Cryogenics, Inc. Horizontal bulk oil separator
WO2009146120A1 (fr) 2008-04-04 2009-12-03 Brooks Automation, Inc. Pompe cryogénique employant des alliages étain-antimoine et procédés d’utilisation
US8978400B2 (en) 2009-11-09 2015-03-17 Sumitomo (Shi) Cryogenics Of America Inc. Air cooled helium compressor
JP2011099669A (ja) * 2009-11-09 2011-05-19 Sumitomo Heavy Ind Ltd 空冷ヘリウムコンプレッサ
US20110107790A1 (en) * 2009-11-09 2011-05-12 Stephen Dunn Air Cooled Helium Compressor
US10240832B2 (en) 2015-12-18 2019-03-26 Sumitomo (Shi) Cryogenic Of America, Inc Helium compressor with dual after-coolers
US11149992B2 (en) 2015-12-18 2021-10-19 Sumitomo (Shi) Cryogenic Of America, Inc. Dual helium compressors
USRE49384E1 (en) 2015-12-18 2023-01-24 Sumitomo (Shi) Cryogenic Of America, Inc. Helium compressor with dual after-coolers
WO2019199591A1 (fr) 2018-04-09 2019-10-17 Brooks Automation, Inc. Refroidisseur cryogénique à entraînement pneumatique
US11209193B2 (en) 2018-04-09 2021-12-28 Edwards Vacuum Llc Pneumatic drive cryocooler
US11732931B2 (en) 2018-04-09 2023-08-22 Edwards Vacuum Llc Pneumatic drive cryocooler
US11913697B1 (en) 2020-06-29 2024-02-27 The United States Of America, As Represented By The Secretary Of The Navy Pneumatically actuated cryocooler

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Publication number Publication date
GB882656A (en) 1961-11-15
FR1215279A (fr) 1960-04-15
GB938182A (en) 1963-10-02
US2966035A (en) 1960-12-27
SE304526B (fr) 1968-09-30
DE1282661B (de) 1968-11-14
DE1401515A1 (de) 1968-12-05
NL233237A (fr)
NL252718A (fr)
NL113898C (fr)

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