US3620029A - Refrigeration method and apparatus - Google Patents
Refrigeration method and apparatus Download PDFInfo
- Publication number
- US3620029A US3620029A US867594A US3620029DA US3620029A US 3620029 A US3620029 A US 3620029A US 867594 A US867594 A US 867594A US 3620029D A US3620029D A US 3620029DA US 3620029 A US3620029 A US 3620029A
- Authority
- US
- United States
- Prior art keywords
- displacer
- fluid
- refrigeration
- chamber
- orifice
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/003—Gas cycle refrigeration machines characterised by construction or composition of the regenerator
-
- 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
- F25B2309/006—Gas cycle refrigeration machines using a distributing valve of the rotary type
Definitions
- a device for cooling refrigeration fluid by expansion comprising a displacer within a closed housing, said housing communicating through an orifice to another closed chamber so that the displacer can force a fluid through the orifice thereby doing work in the refrigeration cycle and conversely, the fluid can return through the orifice to move the displacer in the opposite direction at the proper time in the cycle.
- the invention is characterized in that the refrigeration is accomplished in a simplified manner without auxiliary equipment such as connecting rods, crank shafts, or the like to cycle the displacer.
- the method of producing refrigeration by directly dissipating the expander work to heat by cycling a fluid through an orifice. Cycling of the fluid through the orifice is also the operative means of actuating the displacer.
- the present invention pertains to a method and apparatus for producing cryogenic refrigeration.
- the apparatus employs a displacer that is driven by cycling a volume of a surge fluid through an orifice so that external driving means for the displacer are unnecessary. Work is expended by forcing the surge gas through the orifice into a surge volume chamber whereby the heat generated by such action can be removed by suitable heat exchange.
- the instant invention is an improvement over the prior art devices in that it neither requires an external driving force for the displacer nor does it require continuous high pressure gas and snap-acting spring devices to effect cycling of the displacer.
- a refrigeration cycle of the type employed in the instant invention was first disclosed by Ernest Solvay in German Pat. 39,280 issued May 16, 1887.
- the Solvay cycle does not employ cycling of the displacer against a volume of surge gas that passes reversely through an orifice to effect cycling of the displacer.
- Solvay relied upon external moving forces to actuate the displacer in order to eifect refrigeration.
- the present invention comprises providing a volume of surge gas confined so that it can be cycled between a surge volume chamber and a chamber containing a displacer used to refrigerate or to cool a cryogenic fluid by expansion, the surge chamber and displacer chamber being connected by a small orifice so that the surge volume fluid can be forced reversably through the orifice to effect cycling of the displacer.
- a displacer used to refrigerate or to cool a cryogenic fluid by expansion
- the surge chamber and displacer chamber being connected by a small orifice so that the surge volume fluid can be forced reversably through the orifice to effect cycling of the displacer.
- Included in the apparatus are the necessary valves for admitting and venting the fluid to be cooled as well as regeneration devices to aid in the overall refrigeration cycle.
- the refrigeration cycle disclosed is accomplished by expanding the refrigeration fluid against a volume of confining fluid similar to or other than the refrigeration fluid and separated therefrom.
- FIG. 1 is a schematic diagram showing a first embodiment of an apparatus according to the present invention.
- FIG. 2 is a schematic diagram of a second embodiment according to the present invention showing internal regeneration of the refrigeration fluid.
- FIG. 3 is a schematic diagram of a two-stage displacer according to the present invention.
- FIG. 4 is a schematic diagram of a different two-stage displacer according to the present invention.
- FIG. 5 is a theoretical diagram of the cycle according to the present invention.
- FIG. 6 is a P-V diagram of the actual cycle according to the present invention.
- FIG. 7 is a cross-section diagram of a device constructed according to the present invention.
- FIG. 1 there is shown a device according to the present invention comprising a fluid tight housing 10.
- the housing 10 comprises a first chamber 12 and a second chamber 14. Between the chambers 12 and 14 is an orifice 16.
- Disposed within chamber 12 is a displacer 18 with a sealing member 20 disposed near one end and surrounding the displacer 18 so that a fluid tight seal is achieved between the displacer 18 and walls of chamber 12, thereby separating the warm volume of gas from the volume of cold gas and to prevent leakage therebetween.
- the displacer is free to move between the bottom 22 of chamber 12 and the top 24 of chamber 12.
- the apparatus includes a supply of high pressure fluid (not shown) delivered through conduit 26.
- conduit 26 Disposed in conduit 26 is an inlet valve 28 for controlling the supply of high pressure fluid.
- Conduit 26 is in turn connected to conduit 30 which in turn is connected to a regeneration device 32 which in turn is connected to a conduit 34 and heat exchanger 36 and conduit 38 to the lower end 22 of chamber 12.
- the regenerator 32 is preferably a chamber containing metal screening of small aperture but can also be stacked particles of other materials such as lead spheres as iswell-known in the art.
- Conduit 30 is in turn connected to an exhaust conduit 40, exhaust valve 42, heat exchanger 44 and conduit 46 serve to conduct the exhaust gas out of the system.
- a capillary tube 48 Deposed between the surge volume chamber 14 of housing 10 and conduit 30 is a capillary tube 48 for controlling the pressure of the surge volume chamber.
- the capillary tube is sized so that the pressure in the surge volume chamber is maintained approximately intermediate between the high and low pressure above the displacer 18 at either end of the cycle as will be explained subsequently.
- the supply conduit 26 is connected to a source of high-pressure refrigeration fluid such as helium gas.
- the cycle starts with the displacer 18 in the position shown in FIG. 1 and low pressure gas in the regenerator 32.
- the exhaust valve 42 is closed and the inlet valve 28 is open admitting the refrigeration fluid through conduit 30 through the bottom of the housing 10.
- the gas causes the displacer 18 to rise until the pressure in the space 12, above the displacer 18, is equal to the pressure below the displacer 18.
- the surge volume chamber 14, which is at an intermediate pressure deter mined by the capillary tube, begins to receive gas from above the displacer 18 through the orifice 16. This allows the displacer to rise filling the cold displaced volume with high pressure gas.
- the inlet valve 28 is closed when the displacer 18 reaches the top of its rise, then the exhaust valve 42 is open and the pressure underneath the displacer 18 begins to decrease.
- the expanding gas drops in temperature and is forced through conduit 38, heat exchanger 36, conduit 34, regenerator 32, conduit 30, conduit 40, valve 42, heat exchanger 44, and conduit 46 and away from the system.
- the gas leaving the cold displaced volume is lower in temperature on the average than the gas entering the volume and can thus extract heat from outside the system as it passes through heat exchanger 36.
- the pressure below the displacer 18 decreases to a level less than the pressure of the surge volume chamber 14, the gas in the surge volume chamber 14 leaks back into chamber 12 forcing the displacer to the bottom 22 of the housing 10.
- the exhaust valve 42 is closed, then the inlet valve 28 opened and the cycle is repeated continually thereby achieving continuous refrigeration.
- Heat exchanger 44 is included to remove the excess heat generated in the gas by forcing the gas through the orifice 16.
- the cooled gas passing out through the regenerator 32 cools the regenerator media so that the subsequently incoming gas is precooled thereby making the refrigeration capacity of the system available at a low temperature.
- the capillary tube 48 is included so that the intermediate pressure of the surge volume chamber 14 is maintained at a fairly uniform level. It would be possible to replace the tube with poppet valves or other pressure control devices, however the capillary tube is preferred.
- the surge chamber volume is on the order of ten times greater than the displaced volume and the orifice 16 is sized so that the displacer can be cycled at any desired speed.
- Prior art devices employing gas pressurization or gas balancing can only be controlled by controlling the gas pressure in the incoming conduits or by using direct linkages to the displacer.
- FIG. 2 is identical to the device of FIG. 1 except that the regenerator is contained within the displacer 18 in the area shown as 50.
- the cycle is identical as is the embodiment of FIG. 1 except that the fluid to be refrigerated is admitted and vented from the housing 10 through the side thereof.
- the incoming fluid is conducted to the regenerator 50 by conduit 52 in the displacer 18 and exited therefrom by conduit 54 to the bottom 22' of housing 10.
- a second annular seal 53 aids in directing the refrigeration fluid through the regenerator 50 during the inlet and exhaust portion of the cycle.
- the P-V diagram shown in FIG. is an ideal cycle assuming that the displacer hits both the top 24 and bottom 22 of the chamber 12 in housing 10. However, this is not desirable since it would lead to excessive vibration of the refrigerator. Therefore, prior to hitting the top and bottom of the chamber 12, the respective valves are closed so that the displacer hits neither top nor bottom. This results in a P-V diagram as shown in FIG. 6 which is the actual cycle employed wherein the direction of the displacer is reversed prior to actually hitting either top 24 or bottom 22 of chamber 12 in housing 10.
- FIG. 3 There is shown in FIG. 3 a multiple stage refrigeration device employing a stepped dislacer 54.
- the displacer 54 contatins a large diameter section 56 and a small diameter section 53 and can be fabricated in a single piece.
- Sections 56 and 58 are disposed within complementary sections 60, 62 of housing 64 and are provided with a primary seal 66 and a secondary seal 68.
- the primary seal 66 prevents fluid from the Warm end from leaking to the cold end 72 of displacer section 56 while seal 68 serves to direct the gas from under displacer section 58 through regenerator 73.
- regenerator 74 for the upper displacer section.
- the refrigerator of FIG. 3 is in essence two refrigerators similar to FIG.
- displacer section 56 is about 30 K. and the cold end temperature of displacer section 58 is 6.5 to 7.0 K.
- Heat exchanger 44 serves to cool the surge chamber.
- Heat exchangers 75 and 36' provide means for using the refrigeration produced at the cold ends of displacer sections 56 and 58 respectively.
- the operating cycle is identical for that described in connection with FIG. 1.
- FIG. 3 disclosed a method of varying the refrigeration by varying the diameter of the displacer.
- FIG. 4 shows another method of varying the swept volume by varying the stroke of the second stage of a two-stage displacer. In order to do this a slack coupling 76 is provided between the upper stage 78 and the lower stage 80 of the displacer 79.
- the operation of the device of FIG. 4 is the same as that described above for the device of FIG. 2 except that the gas is conducted to regenerator 84 of second stage 80 through a conduit 86 associated with coupling 76.
- the slack coupling enables a shorter stroke of section 80 in order to achieve the same refrigeration as a device of FIG. 3.
- a minimum temperature of 6.5 to 7.0 K. can be achieved at end 88 of the refrigerator of FIG. 4.
- Refrigeration produced at end 88 of the refrigerator of FIG. 4 and also at end 22' of the refrigerator of FIG. 2 can be used by means of heat exchanges such as well known in the art and therefore not illustrated.
- One such heat exchanger is shown and described in connection with FIG. 7 below.
- FIG. 7 Shown in FIG. 7 is a cross-sectional diagram of a device actually constructed and operated according to the present invention.
- the displacer is slidably disposed within housing 102.
- the displacer 100 is provided with a seal 104 so that the hot end 106 is sealed from the cold end 108 of housing 102.
- a heat exchanger 110 for delivering the refrigeration produced by the displacer.
- a fluid tight cover 112 provided with an orifice 114 and filters 116.
- a surge volume chamber housing 118 Mounted over cover 112 and in fluid tight relation thereto is a surge volume chamber housing 118 defining a surge volume chamber 120.
- the displacer housing 102 and surge chamber housing are mounted on a base plate 122 to effect the fluid tight seal.
- Sealing members 124, 126 are provided for the displacer chamber 102 and surge chamber 118 to aid in maintaining the fluid seal with base plate 122.
- Heat exchanger 110 is connected via conduit 124 to regenerator 126 mounted on base plate 122.
- Regenerator 126 is filled with a regenerator material 128 such as fine Wire screening.
- Regenerator 126 is fitted with the necessary passages 130 and 132 for conducting fluid through the regeneration chamber.
- valve assembly 133 Mounted on base plate 122 above the regenerator and in fluid tight relation thereto is a valve assembly shown generally as 133 consisting of an upper housing 134 containing an inlet port 131 to be connected to a source of high pressure gas (not shown) and a lower housing 136 containing an exhaust port 137 for venting the cooled gas.
- Inlet port 131 communicates with chamber 138 in which is disposed rotary valve 140 for admitting gas to the system through conduit 135 and also for venting gas via port 137 in housing 136.
- a capillary tube 152 is connected between surge chamber 120 and conduit 135 for maintaining pressure in surge chamber 120.
- Motor 146 is driven electrically by means of a source of power (not shown) delivered through electrical conduit 150.
- the motor 146 serves to drive the valve disc 144 to alternately admit high pressure gas to the bottom 108 of housing 102 through regenerator 128 and vent the cooled gas along the same path in accord with the refrigeration cycle described in connection with FIG. 1.
- a device of the type shown in FIG. 7 was operated for 200 hours and produced 25 watts of refrigeration at 77 K. at heat exchanger 110 when operated at 144 revolutions per minute under 350/150 p.s.i.a. helium.
- a refrigerator comprising:
- a fluid tight housing having a generally circular crosssection; said housing divided into a displacer chamber and a fluid surge chamber with an orifice therebetween;
- displacer movably disposed within the displacer chamber, a displacer, said displacer having a cross-section configuration similar to said housing; sealing means disposed around said displacer so that the displacer chamber can have a hot end and a cold end, said hot end adjacent said fluid surge chamber;
- a refrigerator comprising:
- a fluid tight housing having a generally circular crosssection
- said housing divided into a fluid surge chamber, a first displacer chamber with an orfice therebetween and a second displacer chamber;
- sealing means disposed around said first and second dipslacer sections so that the displacer chamber can have a cold end and a hot end associated with each displacer section;
- regenerator is provided with a regeneration medium selected from the group consisting of fine wire screening and metal spheres.
- a refrigerator comprising:
- a fluid tight housing having a generally circular crosssection
- said housing divided into a displacer chamber and a fluid surge volume chamber with an orifice therebetween;
- said displacer having a first section spaced apart from a second section and connected to it by slack coupling means;
- sealing means disposed around said first and second displacer sections so that the displacer chamber can have a cold end and a hot end associated with each displacer section;
- a method of producing refrigeration comprising the steps of:
- a method according to claim 10 wherein said cooled fluid is used to cool the surge gas chamber.
- a method according to claim 10 wherein said supply of refrigeration fluid is controlled by an automatic timing device.
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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)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US86759469A | 1969-10-20 | 1969-10-20 |
Publications (1)
Publication Number | Publication Date |
---|---|
US3620029A true US3620029A (en) | 1971-11-16 |
Family
ID=25350098
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US867594A Expired - Lifetime US3620029A (en) | 1969-10-20 | 1969-10-20 | Refrigeration method and apparatus |
Country Status (6)
Country | Link |
---|---|
US (1) | US3620029A (de) |
CA (1) | CA925715A (de) |
DE (1) | DE2051203C2 (de) |
FR (1) | FR2066265A5 (de) |
GB (1) | GB1330345A (de) |
SE (1) | SE358956B (de) |
Cited By (47)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3877239A (en) * | 1974-03-18 | 1975-04-15 | Hughes Aircraft Co | Free piston cryogenic refrigerator with phase angle control |
US3981155A (en) * | 1975-03-10 | 1976-09-21 | The United States Of America As Represented By The Secretary Of The Air Force | Plasma deposited rider rings for hot displacer |
US4150549A (en) * | 1977-05-16 | 1979-04-24 | Air Products And Chemicals, Inc. | Cryopumping method and apparatus |
US4223540A (en) * | 1979-03-02 | 1980-09-23 | Air Products And Chemicals, Inc. | Dewar and removable refrigerator for maintaining liquefied gas inventory |
WO1981001191A1 (en) * | 1979-10-29 | 1981-04-30 | Oerlikon Buehrle Inc | Valves for cryogenic refrigerators |
WO1981001192A1 (en) * | 1979-10-29 | 1981-04-30 | Oerlikon Buehrle Inc | Cryogenic apparatus |
WO1981001190A1 (en) * | 1979-10-29 | 1981-04-30 | Oerlikon Buehrle Inc | Cryogenic refrigerator with dual control valves |
US4277949A (en) * | 1979-06-22 | 1981-07-14 | Air Products And Chemicals, Inc. | Cryostat with serviceable refrigerator |
US4277951A (en) * | 1980-04-10 | 1981-07-14 | Air Products And Chemicals, Inc. | Cryopumping apparatus |
US4279127A (en) * | 1979-03-02 | 1981-07-21 | Air Products And Chemicals, Inc. | Removable refrigerator for maintaining liquefied gas inventory |
US4310337A (en) * | 1979-10-29 | 1982-01-12 | Oerlikon-Buhrle U.S.A. Inc. | Cryogenic apparatus |
US4333755A (en) * | 1979-10-29 | 1982-06-08 | Oerlikon-Buhrle U.S.A. Inc. | Cryogenic apparatus |
US4335579A (en) * | 1979-09-17 | 1982-06-22 | Aisin Seiki Kabushiki Kaisha | Refrigerating system |
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 |
EP0096391A2 (de) * | 1982-06-07 | 1983-12-21 | Air Products And Chemicals, Inc. | Tiefsttemperatur-Kältemaschine |
US4475345A (en) * | 1982-01-20 | 1984-10-09 | Leybold-Heraeus Gmbh | Refrigerator with pneumatic and working gas-supply control |
US4484458A (en) * | 1983-11-09 | 1984-11-27 | Air Products And Chemicals, Inc. | Apparatus for condensing liquid cryogen boil-off |
US4514204A (en) * | 1983-03-21 | 1985-04-30 | Air Products And Chemicals, Inc. | Bakeable cryopump |
US4530213A (en) * | 1983-06-28 | 1985-07-23 | Air Products And Chemicals, Inc. | Economical and thermally efficient cryopump panel and panel array |
US4538416A (en) * | 1983-09-29 | 1985-09-03 | Air Products And Chemicals, Inc. | Method and apparatus for valve motor actuation of a displacer-expander refrigerator |
US4567943A (en) * | 1984-07-05 | 1986-02-04 | Air Products And Chemicals, Inc. | Parallel wrapped tube heat exchanger |
US4593530A (en) * | 1984-04-10 | 1986-06-10 | Air Products And Chemicals, Inc. | Method and apparatus for improving the sensitivity of a leak detector utilizing a cryopump |
US4606201A (en) * | 1985-10-18 | 1986-08-19 | Air Products And Chemicals, Inc. | Dual thermal coupling |
US4643001A (en) * | 1984-07-05 | 1987-02-17 | Air Products And Chemicals, Inc. | Parallel wrapped tube heat exchanger |
US4697635A (en) * | 1984-07-05 | 1987-10-06 | Apd Cryogenics Inc. | Parallel wrapped tube heat exchanger |
EP0350290A2 (de) * | 1988-07-07 | 1990-01-10 | The BOC Group plc | Tiefsttemperaturkältemaschinen |
US5327733A (en) * | 1993-03-08 | 1994-07-12 | University Of Cincinnati | Substantially vibration-free shroud and mounting system for sample cooling and low temperature spectroscopy |
US5878580A (en) * | 1993-06-03 | 1999-03-09 | Leybold Aktiengesellschaft | Method of operating a cryogenic cooling device, and a cryogenic cooling device suitable for operation by this method |
US6256997B1 (en) | 2000-02-15 | 2001-07-10 | Intermagnetics General Corporation | Reduced vibration cooling device having pneumatically-driven GM type displacer |
EP1304516A2 (de) * | 2001-10-19 | 2003-04-23 | Oxford Magnet Technology Limited | Drehventil |
US20070107442A1 (en) * | 2004-03-08 | 2007-05-17 | Eric Seitz | Wearless valve for cryorefrigerator |
US20070119188A1 (en) * | 2004-01-20 | 2007-05-31 | Mingyao Xu | Reduced torque valve for cryogenic refrigerator |
US20070119189A1 (en) * | 2004-02-11 | 2007-05-31 | Gao Jin L | Three track valve for cryogenic refrigerator |
US20070163272A1 (en) * | 2006-01-18 | 2007-07-19 | Mingyao Xu | Compact integrated buffer for pulse tube refrigerator |
US20080116410A1 (en) * | 2006-11-21 | 2008-05-22 | Sang Kwon Jeong | Buffered rotary valve |
US20080245077A1 (en) * | 2005-06-10 | 2008-10-09 | Sumitomo Heavy Industries, Ltd. | Multiple Rotary Valve For Pulse Tube Refrigerator |
US20130025297A1 (en) * | 2010-04-19 | 2013-01-31 | Sumitomo Heavy Industries, Ltd | Rotary valve and cryogenic refrigerator using same |
US8448461B2 (en) | 2010-10-08 | 2013-05-28 | Sumitomo (Shi) Cryogenics Of America Inc. | Fast cool down cryogenic refrigerator |
JP2013139822A (ja) * | 2008-07-17 | 2013-07-18 | Sumitomo Heavy Ind Ltd | クライオポンプルーバ拡張部 |
CN105135735A (zh) * | 2014-06-05 | 2015-12-09 | 住友重机械工业株式会社 | 斯特林型脉冲管制冷机 |
US20190063790A1 (en) * | 2016-12-16 | 2019-02-28 | Fudan University | Mechanical vibration isolation liquid helium re-condensation low-temperature refrigeration system |
WO2019199591A1 (en) | 2018-04-09 | 2019-10-17 | Brooks Automation, Inc. | Pneumatic drive cryocooler |
US10677498B2 (en) | 2012-07-26 | 2020-06-09 | Sumitomo (Shi) Cryogenics Of America, Inc. | Brayton cycle engine with high displacement rate and low vibration |
US10753653B2 (en) * | 2018-04-06 | 2020-08-25 | Sumitomo (Shi) Cryogenic Of America, Inc. | Heat station for cooling a circulating cryogen |
US11137181B2 (en) | 2015-06-03 | 2021-10-05 | Sumitomo (Shi) Cryogenic Of America, Inc. | Gas balanced engine with buffer |
US11913697B1 (en) | 2020-06-29 | 2024-02-27 | The United States Of America, As Represented By The Secretary Of The Navy | Pneumatically actuated cryocooler |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE8411307U1 (de) * | 1984-04-11 | 1984-07-05 | Leybold-Heraeus GmbH, 5000 Köln | Kaeltemaschine |
DE4318406A1 (de) * | 1993-06-03 | 1994-12-08 | Leybold Ag | Verfahren zum Betrieb eines Refrigerators und für die Durchführung dieses Verfahrens geeigneter Refrigerator |
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US2567454A (en) * | 1947-10-06 | 1951-09-11 | Taconis Krijn Wijbren | Process of and apparatus for heat pumping |
NL233237A (de) * | 1957-11-14 | |||
US3074244A (en) * | 1961-04-12 | 1963-01-22 | Malaker Lab Inc | Miniature cryogenic engine |
GB1050270A (de) * | 1963-11-12 | |||
NL6402127A (de) * | 1964-03-04 | 1965-09-06 | ||
US3218815A (en) * | 1964-06-17 | 1965-11-23 | Little Inc A | Cryogenic refrigeration apparatus operating on an expansible fluid and embodying a regenerator |
US3312072A (en) * | 1965-06-11 | 1967-04-04 | William E Gifford | Method and apparatus for refrigeration utilizing sterling cycle type of operation |
US3321926A (en) * | 1965-12-03 | 1967-05-30 | Little Inc A | Fluid-actuated cryogenic refrigerator |
-
1969
- 1969-10-20 US US867594A patent/US3620029A/en not_active Expired - Lifetime
-
1970
- 1970-10-14 CA CA095525A patent/CA925715A/en not_active Expired
- 1970-10-15 GB GB4916070A patent/GB1330345A/en not_active Expired
- 1970-10-19 DE DE2051203A patent/DE2051203C2/de not_active Expired
- 1970-10-19 SE SE14053/70A patent/SE358956B/xx unknown
- 1970-10-20 FR FR7037860A patent/FR2066265A5/fr not_active Expired
Cited By (71)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3877239A (en) * | 1974-03-18 | 1975-04-15 | Hughes Aircraft Co | Free piston cryogenic refrigerator with phase angle control |
US3981155A (en) * | 1975-03-10 | 1976-09-21 | The United States Of America As Represented By The Secretary Of The Air Force | Plasma deposited rider rings for hot displacer |
US4150549A (en) * | 1977-05-16 | 1979-04-24 | Air Products And Chemicals, Inc. | Cryopumping method and apparatus |
US4223540A (en) * | 1979-03-02 | 1980-09-23 | Air Products And Chemicals, Inc. | Dewar and removable refrigerator for maintaining liquefied gas inventory |
US4279127A (en) * | 1979-03-02 | 1981-07-21 | Air Products And Chemicals, Inc. | Removable refrigerator for maintaining liquefied gas inventory |
US4277949A (en) * | 1979-06-22 | 1981-07-14 | Air Products And Chemicals, Inc. | Cryostat with serviceable refrigerator |
US4335579A (en) * | 1979-09-17 | 1982-06-22 | Aisin Seiki Kabushiki Kaisha | Refrigerating system |
US4305741A (en) * | 1979-10-29 | 1981-12-15 | Oerlikon-Buhrle U.S.A. Inc. | Cryogenic apparatus |
WO1981001190A1 (en) * | 1979-10-29 | 1981-04-30 | Oerlikon Buehrle Inc | Cryogenic refrigerator with dual control valves |
US4294077A (en) * | 1979-10-29 | 1981-10-13 | Oerlikon-Buhrle U.S.A. Inc. | Cryogenic refrigerator with dual control valves |
US4294600A (en) * | 1979-10-29 | 1981-10-13 | Oerlikon-Buhrle U.S.A. Inc. | Valves for cryogenic refrigerators |
WO1981001192A1 (en) * | 1979-10-29 | 1981-04-30 | Oerlikon Buehrle Inc | Cryogenic apparatus |
US4310337A (en) * | 1979-10-29 | 1982-01-12 | Oerlikon-Buhrle U.S.A. Inc. | Cryogenic apparatus |
US4333755A (en) * | 1979-10-29 | 1982-06-08 | Oerlikon-Buhrle U.S.A. Inc. | Cryogenic apparatus |
WO1981001191A1 (en) * | 1979-10-29 | 1981-04-30 | Oerlikon Buehrle Inc | Valves for cryogenic refrigerators |
US4277951A (en) * | 1980-04-10 | 1981-07-14 | Air Products And Chemicals, Inc. | Cryopumping apparatus |
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Also Published As
Publication number | Publication date |
---|---|
SE358956B (de) | 1973-08-13 |
CA925715A (en) | 1973-05-08 |
DE2051203A1 (de) | 1971-05-06 |
GB1330345A (en) | 1973-09-19 |
FR2066265A5 (de) | 1971-08-06 |
DE2051203C2 (de) | 1981-10-01 |
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AS | Assignment |
Owner name: APD CRYOGENICS INC., A CORP OF PA. Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:AIR PRODUCTS AND CHEMICALS, INC., A CORP OF DE.;REEL/FRAME:004686/0713 Effective date: 19870310 Owner name: APD CRYOGENICS INC.,PENNSYLVANIA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:AIR PRODUCTS AND CHEMICALS, INC.;REEL/FRAME:004686/0713 Effective date: 19870310 |