US3902328A - Method of refrigeration combining two thermodynamic cycles and a corresponding cryogenic machine - Google Patents

Method of refrigeration combining two thermodynamic cycles and a corresponding cryogenic machine Download PDF

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US3902328A
US3902328A US484101A US48410174A US3902328A US 3902328 A US3902328 A US 3902328A US 484101 A US484101 A US 484101A US 48410174 A US48410174 A US 48410174A US 3902328 A US3902328 A US 3902328A
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fluid
expansion
piston
thermodynamic
cycle
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Gerard Claudet
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Commissariat a lEnergie Atomique et aux Energies Alternatives CEA
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    • 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
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
    • F02G1/0445—Engine plants with combined cycles, e.g. Vuilleumier
    • 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
    • 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
    • F02G2244/00—Machines having two pistons
    • F02G2244/50—Double acting piston machines
    • 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
    • F02G2250/00—Special cycles or special engines
    • F02G2250/18—Vuilleumier cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1408—Pulse-tube cycles with pulse tube having U-turn or L-turn type geometrical arrangements
    • 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
    • F25B9/145—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 pulse-tube cycle

Definitions

  • PATENTED EP 2191s sumuufg 9s wv g v Eii! m METHOD OF REFRIGERATION COTNIING TWU THERMUDYNAMIC CYCLES AND A CURRESPONDKNG CRYOGENTC MACHINE
  • This invention relates to a method of refrigeration which combines two thermodynamic cycles and a cryogenic machine for carrying out said method.
  • One notable application of the invention is in the field of cryogenics.
  • thermodynamic cycles which permit power extraction at low temperature usually entail four basic operations, namely: compression, cooling, expansion and reheating.
  • the Claude cycle which belongs to the first category of continuous circulation cycles is of interest in medium-power and high-power installations since it has high efficiency and permits direct utilization of the continuously circulating gas for the extraction of power.
  • the cold gas is expanded and supplies mechanical work which is taken off either on a turbine shaft when the installation is of large size or by means of a piston machine.
  • the expansion unit is always of very delicate design and often limits the practical applications of this cycle.
  • the invention proposes a composite solution in which two different cycles are employed in close conjunction with each other so that certain operational stages of one cycle control operational stages of the other cycle.
  • the present invention is directed to a method of refrigeration of the type which consists in causing a fluid to undergo a thermodynamic cycle comprising the operations of compression, cooling, expansion and reheating.
  • the method essentially consists in subjecting two distinct fluid circulations to different but coupled thermodynamic cycles, the effect of at least one operation in each cycle being such as to initiate one operation of the other cycle.
  • the invention preferably combines a cycle of the continuous fluid-circulation type with an alternate-circulation cycle.
  • the invention contemplates the use of the Claude or Brayton cycles; in the case of the cycles of the second category, the invention recommends the use of the Stirling or Gifford-McMahon cycles or the Taconis or Vuilleumier cycles or alternatively the so-called pulse-tube cycle.
  • the cooling power delivered by means of a method of this type can be extracted from one of the cycles such as, for example but not exclusively, from the continuous fluid-circulation cycle.
  • the cooling power delivered by the other cycle is employed for the purpose of balancing the temperatures between the different parts of the machine but can also be partially extracted.
  • the present invention is also directed to a cryogenic machine for carrying out the method which has just been defined.
  • Said machine essentially comprises two coupled cryogenic machines which operate in accordance with different thermodynamic cycles with sepa' rate fluids, at least one of the operations performed in each machine being intended to control elements belonging to the other machine.
  • One of the machines is preferably of the type involving continuous circulation of a first fluid and comprises in particular an alternating expansion unit and the other machine is preferably of the type in which provision is made for alternate circulation of a second fluid, the variations in pressure of said second fluid being such as to control said alternating expansion unit pneumatically.
  • said alternating expansion unit is of the expansion piston type.
  • the alternate-circulation machine can be of the heataccumulator type and can further comprise a displacer piston, in which case said displacer piston is coupled to the expansion piston of the continuouscirculation machine.
  • FIG. 1 is a schematic diagram of a cryogenic machine which operates in accordance with the Claude cycle
  • FIG. 2 is a schematic diagram of a cryogenic machine which operates in accordance with the Brayton cycle
  • FIG. 3 is a diagram of an alternating piston-type expansion unit
  • FIG. 4 is a schematic diagram of an altematecirculation cryogenic machine
  • FIGS. 5, 6, 7 and 8 represent alternative forms of alternate-circulation machines which operate respectively in accordance with the Stirling cycle, the Gifford- McMahon type, the Taconis type or the Vuilleumier type and of the pulse-tube type;
  • FIG. 9 is a schematic diagram of the cryogenic machine in accordance with the invention.
  • FIG. 10 is a diagram of an alternative embodiment in which an expansion-piston machine and a displacerpiston machine are combined;
  • FIG. 11 shows the different positions of the expansion and displacer pistons during the operating cycle of the machine shown in FIG. 10.
  • FIG. 1 a general diagram of a cryogenic installation which operates in accordance with the Claude cycle.
  • a compressor 2 and heat exchangers 4 An expansion unit 6 produces action on a portion of the circulating fluid whilst the other portion is directed towards a valve 8 in which the Joule-Thomson expansion which takes place therein results in liquefaction of the gas.
  • FIG. 2 shows diagrammatically a cryogenic machine which operates in accordance with the Brayton cycle and differs from the previous machine in that the entire quantity of fluid compressed by the compressor 10 passes through the expansion unit 12, the cooling power being utilized through the element 14.
  • the expansion units 6 and 12 of the installations referred-to above can be alternating and each comprise a piston as shown in FIG. 3.
  • Said piston is designated by the reference 20 and is capable of displacement within a cylinder 22, the top end of which is fitted with gas intake and exhaust means 24 and 26 (disc-valves, poppet valves, check-valves and the like).
  • the intake means 24 are connected to means 28 for supplying fluid under the conditions of temperature and pressure which are adapted to a cryogenic machine of the continuous-circulation type, that is to say in actual fact under conditions of high pressure and low temperature.
  • the chambers 30 and 32 are at very different temperatures, thus giving rise to a transfer of heat to the chamber 30 and impairing the performances of the machine to an even greater extent.
  • One of the objects of the invention is precisely to eliminate these disequilibria by virtue of the incorporation of a second machine which is preferably of the alternate-circulation type and so designed that the conditions of pressure and temperature of the fluid within the chamber 32 which is located beneath the alternating piston are close to the conditions of temperature and pressure of the fluid within the chamber 30 which forms part of the continuous-circulation machine.
  • an enclosure 40 comprises a heat accumulator 42 located between two chambers 44 and 46 between which a fluid circulates in an alternate flow motion.
  • This flow motion is produced by means 48 which can assume a number of different forms illustrated by the following figures.
  • said means comprise a piston 50 actuated by a stem 52 which is co trolled by mechanical means (not illustrated in the figure); a displacer piston 54 is actuated by a piston-rod 56 which is controlled by mechanical means (also omitted from the figure).
  • the heat accumulator can be located either within the displacer piston 54 or in an associated connecting-tube which is shown on the righthand side of the figure in chaindotted lines.
  • This diagram corresponds to a machine which operates in accordance with the so-called Stirling cycle. As a result of their combined movements, the moving displacer piston and the lower piston 50 controls the alternate flow of gas through the heat accumulator.
  • the means 48 shown in FIG. 4 are constituted by gas intake means 60 and gas discharge means 62, by a high-pressure gas reservoir 64 and by a lowpressure gas reservoir 66; a displacer piston 68 which contains the heat accumulator is also actuated by a piston-rod 70 controlled by mechanical means (not shown).
  • This figure corresponds to the diagram of a machine which operates in accordance with the socalled Gifford-McMahon cycle.
  • FIG. 7 shows a third alternative embodiment in which the means for producing alternate circulation of the fluid are constituted by a moderately hot source 72 and a very hot source 74 between which the thermal compressions take place.
  • the displacer 76 is also endowed with an alternating movement by means of the piston-rod 78 which is controlled in a suitable manner.
  • FIG. 8 also shows an alternate-circulation machine but no longer comprises a displacer piston. This is replaced by a pulse-tube comprising a stationary heat accumulator 80 and a dead space 82.
  • the means for producing alternating pressure variations beneath the accumulator 80 can be of several different types as shown in FIGS. 5 to 7; by way of explanation, FIG. 8 shows an alternative embodiment in which said means are constituted by a moving piston 84.
  • cryogenic machine in accordance with the 'invention will now be described and will accordingly serve to define the method of refrigeration which is employed by this machine.
  • FIG. 9 The general diagram of the cryogenic machine in accordance with the invention is illustrated in FIG. 9.
  • a first cryogenic machine 100 and a second cryogenic machine 102 which utilize different thermodynamic cycles such as a Claude cycle in the case of the machine 100 and a Stirling cycle in the case of the machine 102, these cycles being mentioned solely by way of example.
  • the two machines aforesaid are closely coupled together by means which are indicated sche matically by the stage 104, with the result that at least one operation performed within each machine controls elements which form part of the other machine.
  • the coupling element 104 can be simply constituted by a member 110 which couples the piston 106 and 108 in rigidly fixed relation. In this manner, the variations in the pressures of the fluid contained in the machine 102 which result in displacement of the displacer piston 108 will have the effect of initiating the movement of the piston 106 at the same time.
  • the injection of the first fluid into the cryogenic machine 100 under high pressure which has the effect of moving the piston 106 downwards also has the effect of displacing the piston 108 of the second machine 102. If the zone 104 is given a suitable shape.
  • the fluid of the machine 102 which follows a thermodynamic cycle can by substantially under the same conditions of temperature and pressure as the fluid of the machine 100, with the result that the disequilibria mentioned in the foregoing in connection with the machine of the first category are eliminated.
  • FIG. 10 An expansion-piston machine is combined with a displacer-piston machine in the embodiment shown in this figure, in which the cryogenic machine comprises:
  • a casing 120 in which the walls are constituted by cylinders having different diameters and which are closed at one end by a cover 122 fitted with means 124 and 126 respectively for admission and discharge of a first fluid and at the other end by a moving piston 128;
  • an expansion-displacer piston 130 which corresponds in shape to said walls and is capable of back-and-forth motion within the casing; said piston delimits at one end a chamber C, which is filled with said first fluid and at the other end a chamber C at least one chamber C being delimited in the intermediate portion of said piston at the level of the changes in diameter of said cylinders; the chambers C and C are filled with a second fluid;
  • means 136 for supplying a first fluid under the conditions which are adapted to a continuous-circulation machine
  • the machine aforesaid therefore comprises a first cryogenic machine 140 of the type which operates in accordance with the Claude cycle and a second cryogenic machine 142 of the type which operates in accordance with the Stirling cycle, these machines being provided with a common piston which performs at the same time the function of expansion piston for the Claude-type machine and of displacer piston for the Stirling-type machine.
  • FIG. 1 l shows the positions of the different components during the operating cycle.
  • Four instantaneous positions are designated by the references a, b, c, d, between which there are four operational stages designated respectively by the references I, II, III and IV.
  • the stage I is the compression stage for the fluid contained in the chamber C compression is produced by the upward motion of the piston 128.
  • the heat accumulators are cold as a result of the previous stage IV.
  • the admission and discharge valves 124 and 126 are closed.
  • the upward motion of the piston 128 causes the upward motion of the displacerexpansion piston 130, thereby compressing the fluid contained in the chamber C
  • the end of stage I is illustrated in the diagram b.
  • the admission valve 124 opens and this is the beginning of stage II.
  • the opening of the admission valve 124 initiates the admission of the first fluid under a high pressure, thereby causing the expansion-displacer piston 130 to return downwards; this movement results in transfer of the fluid which was contained in the chamber C to the chambers C.
  • the mean temperature of the second fluid is reduced by reason of the fact that it has passed over the cold heat accumulators.
  • the volume of said second fluid decreases and this has the effect of moving; the displacer-expansion piston 130 towards the piston 128, this effect being enhanced by the admission of the first fluid under high pressure.
  • the positions of the components are as shown in FIG. 0.
  • stage III The closure of the admission valve and the downward motion of the piston 1128 give rise in stage III to expansion of the gases contained in the chambers C C and C
  • the expansion-displacer piston 130 At the end of stage III, the expansion-displacer piston 130 is in the bottom position and, at the end of travel, the exhaust valve 126 :is open as shown in FIG. a.
  • stage IV the beginning of upward motion of the piston 128 causes the upward return of the expansiondisplacer piston 130 and the transfer of the cooled fluid from the chambers C and the chamber C
  • This fluid increases in volume at the time of reheating and accordingly permits the continued upward motion of the expansion-displacer piston, which also results in discharge of the first fluid contained in the chamber C until the instant of closure of the exhaust valve 126.
  • the piston 128 which had moved only to a slight extent is restored to the position shown in FIG. a and the cycle continues.
  • the pressure is the same at any moment (subject to pressure drops) at all points of the casing 120.
  • it is only necessary to obtain between the chambers C and C a low standard of pressure-tightness which does not give rise to a substantial degree of friction.
  • the heat losses to the chamber C are completely eliminated if the general dimensions of the circuits are such that the temperature of the fluid within the chamber C is equal to the temperature of one of the chambers C, namely the nearest chamber C, for example.
  • the cooling power need be extracted only from the first fluid but may also be extracted from the second fluid either wholly or in part. If the machine 142 comprises a plurality of stages at different temperatures, the power can be extracted at different temperature levels. In some alternative forms of construction, the dimensions of the machines 140 and 142 can be such that the alternate-circulation machine supplies the cooling power whislt the power delivered by the continuouscirculation machine is employed only for the purpose of ensuring equilibria.
  • FIGS. 10 and l 1 there is shown by way of explanation an expansion-displacer piston 130 which contains the ducts 132 and the heat accumulators 134 but it would not constitute any departure from the scope of the invention if said ducts and accumulators were placed outside the casing 120.
  • FIG. 5 had shown an alternative form of construction in which the heat accumulator was located outside the main casing.
  • the means for varying the pressure of the fluid contained in the chamber C are shown in FIG. and 11 in the form of a piston 128.
  • said means can take different forms and can in particular comprise sets of check-valves or control valves which put the chamber C alternatively in communication with two reservoirs at different pressures (as shown in dotted lines in FIG. 10 and designated by the references 150 and 152) in order to utilize the Gifford-McMahon cycle; but it would also be possible to employ a cryogenic machine 142 of the Taconis or Vuilleumier type or alternatively a pulse-tube machine.
  • expansion chamber C which is fitted with intake and exhaust valves and shown diagrammatically in FIGS. 10 and 11 can be of the type described in French Pat. No. 2,123,611, issued Jan. 25, 1971.
  • the two gases of the cryogenic machines can advantageously be the same.
  • the length of service life of the cryogenic machine according to the invention is now dependent only on the portion which operates at ambient temperature. In point of fact, this portion is even more simple than in the altemate-circulation machines of the prior art which are employed alone since it is no longer necessary to control the displacer piston by means of a rod and mechanical means. The service life is therefore appreciably longer than that of known machines.
  • thermodynamic cycle comprising the operations of compression, cooling, expansion and reheating, wherein two distinct fluid circulations are subjected to different but coupled thermodynamic cycles, the effect of at least one operation in each cycle being such as to initiate one operation of the other cycle.
  • said continuous-circulation fluid is subjected to any one of the cycles of the group comprising the Claude and Brayton cycles and wherein said alternate-circulation fluid is subjected to one of the cycles of the group comprising the Stirling cycle, the Gifford-McMahon cycle, the Taconis cycle, the Vuilleumier cycle and the pulse tube cycle.
  • a compound machine combining two coupled cryogenic machines which operate in accordance with different thermodynamic cycles with separate fluids comprising:
  • thermodynamic means for causing a first compressible refrigerating fluid medium to undergo a cycle in which it is subjected to the operations of, successively, compression, cooling, expansion, and reheating; means for utilizing said reheating operation of said first thermodynamic means to extract a refrigerating effect from the compound machine;
  • thermodynamic means for causing a second compressible refrigerating fluid medium to undergo a cycle in which it is subjected to the operations of, successively, compression, cooling, expansion, and reheating;
  • thermodynamic means being so constituted and equipped so as to provide coupling means for coupling said first and second thermodynamic means in such a way that at least one of said operations of each of said first and second thermosaid thermodynamic means is constituted by means for causing the variations in pressure of said second fluid to control said alternating expansion unit pneumatically.
  • thermodynamic means is of the heat accumulator type.
  • thermodynamic means comprises in particular an expansion piston and wherein said second thermodynamic means further comprises a displacer piston, said displacer piston being rigidly fixed to said expansion piston.
  • a cryogenic machine according to claim 9, wherein said machine comprises:
  • thermodynamic means in which the side walls of said casing are constituted at one end by a cover fitted with means for admission and discharge of said first fluid and at the other end by a moving piston;
  • expansion-displacer piston constituting in combined form said expansion piston and said displacer piston, which expander-displacer piston corresponds in shape to said casing walls and is capable of back-andforth motion within said casing, said expansion-displacer piston being so arranged as to delimit at one end with said cover a first chamber (C which is filled with said first fluid and at the other end with said moving piston a second chamber (C at least one intermediate chamber (C) being delimited in the intermediate portion of said expansion'displacer piston at the level of the changes in diameter of said cylinders, said intermediate and second chambers (C and C being filled with said second fluid;
  • a cryogenic machine according to claim 9, wherein said machine comprises:
  • thermodynamic means in which the side walls of said casing are constituted by cylinders having different diameters and which is closed at one end by a cover fitted with means for admission and discharge of said first fluid and at the other end by means for admission and discharge of said second fluid;
  • expansion-displacer piston constituting in combined form said expansion piston and said displacer piston, which expansion-displacer piston corre sponds in shape to said walls and is capable of back-and-forth motion within said casing, said expansion displacer piston. being so arranged as to delimit at one end with said cover a chamber (C which is filled with said first fluid and at the other end with means for supplying said second fluid to a chamber (C at least one chamber (C) being delimited in the intermediate p rtion of said expan sion-displacer piston at the level of the changes in diameter of said cylinders;
  • a cryogenic machine according to claim 6, wherein the first and second fluids aforesaid are identical in composition.
  • a cryogenic machine wherein said communication ducts between said intermediate and second chambers (C and C and the heat accumulators are located within the expansiondisplacer piston.
  • thermodynamic means are so dis posed as to maintain the temperatures of said first chamber (C and of one of said intermediate chambers (C) substantially equal.
  • a cryogenic machine wherein said communication ducts between said intermediate and second chambers (C and C and the heat accumulators are located within the expansiondisplacer piston.
  • thermodynamic means are so disposed as to maintain the temperatures of said first chamber (C and of one of said intermediate chambers (C) substantially equal.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US484101A 1973-07-06 1974-06-28 Method of refrigeration combining two thermodynamic cycles and a corresponding cryogenic machine Expired - Lifetime US3902328A (en)

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US (1) US3902328A (de)
JP (1) JPS5038155A (de)
DE (1) DE2432508A1 (de)
FR (1) FR2236152B1 (de)
GB (1) GB1456420A (de)
IT (1) IT1014476B (de)
NL (1) NL7409116A (de)

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US4277948A (en) * 1980-06-27 1981-07-14 The United States Of America As Represented By The Secretary Of The Army Cryogenic cooler with annular regenerator and clearance seals
US4345437A (en) * 1980-07-14 1982-08-24 Mechanical Technology Incorporated Stirling engine control system
US4350012A (en) * 1980-07-14 1982-09-21 Mechanical Technology Incorporated Diaphragm coupling between the displacer and power piston
US4387567A (en) * 1980-07-14 1983-06-14 Mechanical Technology Incorporated Heat engine device
US4387568A (en) * 1980-07-14 1983-06-14 Mechanical Technology Incorporated Stirling engine displacer gas bearing
US4389844A (en) * 1981-06-11 1983-06-28 Mechanical Technology Incorporated Two stage stirling engine
US4408456A (en) * 1980-07-14 1983-10-11 Mechanical Technolgy Incorporated Free-piston Stirling engine power control
US4418533A (en) * 1980-07-14 1983-12-06 Mechanical Technology Incorporated Free-piston stirling engine inertial cancellation system
US5488830A (en) * 1994-10-24 1996-02-06 Trw Inc. Orifice pulse tube with reservoir within compressor
US5642623A (en) * 1995-02-23 1997-07-01 Suzuki Shokan Co., Ltd. Gas cycle refrigerator
US5711157A (en) * 1995-05-16 1998-01-27 Kabushiki Kaisha Toshiba Cooling system having a plurality of cooling stages in which refrigerant-filled chamber type refrigerators are used
US5735127A (en) * 1995-06-28 1998-04-07 Wisconsin Alumni Research Foundation Cryogenic cooling apparatus with voltage isolation
CN102288005A (zh) * 2011-06-13 2011-12-21 广州赛能冷藏科技有限公司 一种蓄冷热交换器的内外压力平衡装置
US20120085121A1 (en) * 2010-10-08 2012-04-12 Ralph Longsworth Fast Cool Down Cryogenic Refrigerator
US20150176867A1 (en) * 2013-12-19 2015-06-25 Sumitomo (Shi) Cryogenics Of America, Inc. HYBRID BRAYTON - GIFFORD-McMAHON EXPANDER
US11215385B2 (en) 2015-01-28 2022-01-04 Sumitomo (Shi) Cryogenic Of America, Inc. Hybrid Gifford-McMahon-Brayton expander

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AT411731B (de) * 2002-12-06 2004-05-25 Hubert Brugger Magnetfeldmatte zur magnetfeldbehandlung

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US10794616B2 (en) * 2013-12-19 2020-10-06 Sumitomo (Shi) Cryogenic Of America, Inc. Hybrid Brayton—Gifford-McMahon expander
US11215385B2 (en) 2015-01-28 2022-01-04 Sumitomo (Shi) Cryogenic Of America, Inc. Hybrid Gifford-McMahon-Brayton expander

Also Published As

Publication number Publication date
IT1014476B (it) 1977-04-20
JPS5038155A (de) 1975-04-09
FR2236152B1 (de) 1976-06-18
NL7409116A (nl) 1975-01-08
GB1456420A (en) 1976-11-24
DE2432508A1 (de) 1975-01-23
FR2236152A1 (de) 1975-01-31

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