EP0747644A2 - Cryostat Joule-Thomson - Google Patents

Cryostat Joule-Thomson Download PDF

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Publication number
EP0747644A2
EP0747644A2 EP96108475A EP96108475A EP0747644A2 EP 0747644 A2 EP0747644 A2 EP 0747644A2 EP 96108475 A EP96108475 A EP 96108475A EP 96108475 A EP96108475 A EP 96108475A EP 0747644 A2 EP0747644 A2 EP 0747644A2
Authority
EP
European Patent Office
Prior art keywords
temperature
cryostat
needle valve
load
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.)
Withdrawn
Application number
EP96108475A
Other languages
German (de)
English (en)
Other versions
EP0747644A3 (fr
Inventor
Matthew M. Skertic
Joseph L. Hlava
Daniel W. Brunton
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Raytheon Co
Original Assignee
Hughes Missile Systems Co
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
Application filed by Hughes Missile Systems Co filed Critical Hughes Missile Systems Co
Publication of EP0747644A2 publication Critical patent/EP0747644A2/fr
Publication of EP0747644A3 publication Critical patent/EP0747644A3/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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
    • F25B9/02—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect
    • 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
    • F25B2309/02—Gas cycle refrigeration machines using the Joule-Thompson effect
    • F25B2309/022—Gas cycle refrigeration machines using the Joule-Thompson effect characterised by the expansion element

Definitions

  • the present invention relates to Joule-Thomson cryostats. More specifically, the present invention relates systems and techniques for improving the performance of Joule-Thomson cryostats.
  • a cryostat is an apparatus which provides a localized low-temperature environment in which operations or measurements may be carried out under controlled temperature conditions.
  • Cryostats are used to provide cooling of infrared detectors in guided missiles, for example, where detectors and associated electronic components are often crowded into a small containment package.
  • Cryostats are also used in superconductor systems where controlled very low temperatures are required for superconductive activity.
  • a Joule-Thomson cryostat is a cooling device that uses a valve (known in the art as a "Joule-Thomson valve") through which a high pressure gas is allowed to expand via an irreversible throttling process in which enthalpy is conserved, resulting in lowering of its temperature.
  • a valve known in the art as a "Joule-Thomson valve”
  • the simplest form of a conventional Joule-Thomson cryostat typically had a fixed-size orifice in the heat exchanger at the cold end of the cryostat such that cooling by the cryostat was unregulated.
  • the input pressure and internal gas flow dynamics established the flow parameters of the coolant through the cryostat.
  • the conventional Joule-Thomson cryostat is a simple apparatus in that it has no moving parts, the inherent, uncontrolled flow characteristics make the fixed-orifice type cryostat unsuitable for many applications where rapid cool-down and long cooling durations from a limited size gas supply source are required. Rapid cool-down requires high rate gas flow and a large size orifice, while long cooling durations require low gas flow rates and a small size orifice. These two conditions cannot be simultaneously met in a fixed orifice cryostat.
  • cryostats with internal, passive, thermostatic control of variable orifice size have been used. These cryostats have the ability to start cool-down with the maximum orifice size, thereby providing high rate gas flow and refrigeration for rapid cool-down. After cool-down is achieved, the orifice size is reduced for minimal gas flow rate and refrigeration necessary for the thermal load.
  • a thermostatic element within the mandrel of the apparatus provides self-regulation of gas flow based upon the temperature in and around the gas plenum chamber. The cooling rate is proportional to the mass flow rate of gas through the cryostat.
  • the thermostatic element which can be a gas-filled bellows or a segment of material which contracts or expands based upon temperature, is coupled to a demand-flow needle valve mechanism. As the temperature drops, the bellows is adapted to contract and cause the needle to extend into and partially close the Joule-Thompson orifice. At the predetermined critical temperature, the bellows thermostat mechanism can close the needle valve entirely. As the temperature rises, the bellows expands again and actuates the valve mechanism, allowing new coolant flow through the orifice and ultimately to the heat load.
  • thermostat bellows mechanism and similar substitute devices that rely upon expansion and contraction of materials, such as certain plastics
  • materials such as certain plastics
  • cryostats have been found to be non- proportional in their gas flow regulation over the expected full range of operation.
  • cryostat will react differently using different cryogens. Thus, the system performance will be dependent upon the specific cryogen in use during any single operation. If a substitute coolant is used in place of that for which the thermal contraction link is designed, the cryostat will seek the design set temperature and may repeatedly fail.
  • thermophonics a type of thermal noise, known as thermophonics
  • any of these exemplary conditional aspects can result in a premature closing or undesired variations in the needle valve positioning and gas flow rate. This forces a manufacturing design of a multiplicity of Joule-Thomson cryostat components tailored to both heat load factors and coolant parameters.
  • an active mechanism for cryostats which can use the sensed temperature of the thermal load, and not just the gas plenum chamber temperature, to adjust the gas expansion valve orifice size setting from maximum opening during cool-down to a reduced minimal opening for sustained cooling of the thermal load.
  • an active mechanism for cryostats to provide stable, time-averaged, proportional control of the gas expansion valve orifice size for stable gas flow and, therefore, stable refrigeration rate and temperature control.
  • this control should be able to adjust to changing heat load and input pressure conditions, as well as changing thermal environments in a continuous, gradual and non- abrupt manner, which maintains a stable cold temperature.
  • this control should be able to work with multiple coolant gases and provide a stable cold temperature and optimal performance.
  • an active mechanism for cryostats that minimizes susceptibility to temperature fluctuations caused by outside environmental effects, such as inertial accelerations, or to internal thermal waves, or to pressure variations within the plenum chamber.
  • the need in the art is addressed by the present invention which provides an active gas throttling mechanism for a cryostat, using a needle valve controlled, Joule-Thomson effect cryostat to cool a heat load.
  • the inventive apparatus includes an actuator device connected, to a needle valve, for controlling the flow of a coolant therethrough.
  • a temperature sensor is connected to the heat load in proximity thereto. The sensor provides a signal indicative of sensed temperature.
  • a servo-controller receives the signal and regulates the flow of coolant to the actuator device in response thereto.
  • the invention provides a closed-loop method for controlling refrigeration of a thermal load by a Joule-Thomson effect cryostat comprising the steps of: (a) sensing proximate temperature of the thermal load, (b) transmitting a first signal related to the proximate temperature, (c) converting the signal to a second signal for regulating flow of coolant in the cryostat, and (d) adjusting the flow of coolant in direct relation to the first signal.
  • FIG. 1A is a cross-sectional, plan (side) view of a typical conventional cryostat.
  • FIG. 1B is a cross-section, plan view (side) of a typical demand-flow needle valve as utilized in the typical conventional cryostat of FIG 1A.
  • FIG. 2A is a depiction of the present invention in a cross-section, plan view (side) as incorporated in a Joule-Thomson cryostat.
  • FIG. 2B is a detail depiction of a portion of the present invention as shown in FIG. 2A.
  • FIG. 3 is a schematic diagram of the present invention as shown in FIG. 2A.
  • FIG. 4 is a schematic flow chart diagram of the operation of the present invention as shown in FIGS. 2 and 3.
  • FIG. 5 is an alternative embodiment of the present invention as shown in FIG. 2A.
  • FIG. 6 is a schematic flow chart diagram of the operation of the alternative embodiment of the present invention as shown in FIG. 5.
  • FIGS. 1A and 1B A typical conventional Joule-Thomson cryostat 10 is shown in FIGS. 1A and 1B.
  • a coolant such as high pressure argon or nitrogen gas or even air, is introduced through a gas inlet fitting 1 into a recuperative heat exchanger 3 that encompasses a support mandrel 5 inside a cold finger section 7 of a dewar package 9.
  • the heat exchanger 3 basically comprises counterflow finned metal tubing 4 wrapped around the mandrel 5, that allows the high pressure gas to cool significantly as it moves toward the lower end of the cold finger section 7.
  • the heat exchanger tubing 4 terminates in an orifice 16 at the lower end of the mandrel 5, commonly referred to as the cold end of the cryostat.
  • the orifice 16 acts as a Joule-Thomson gas throttling valve. As the gas passes through the orifice 16 and enters the surrounding gas plenum chamber 29, it expands to a low pressure gas and creates a liquid form. The evaporated liquid and low pressure gas are used to cool the thermal load 15 which is located adjacent the dewar window 11. The cooling of the load is accomplished by a liquid coolant spray from the orifice 16 onto the portion of cold finger 7 positioned in contact with thermal load 15. The gas from the chamber 29 is recycled through another low pressure branch of the heat exchanger 3 before exiting into the atmosphere through exit port 13 at the upper, of warm end, of the cryostat 10.
  • the simplest form of a conventional Joule-Thomson cryostat typically had a fixed-size orifice 16 in the heat exchanger 3 at the cold end of the cryostat such that cooling by the cryostat was unregulated.
  • the input pressure and internal gas flow dynamics established the flow parameters of the coolant through the cryostat.
  • the inherent, uncontrolled flow characteristics make the fixed-orifice type cryostat unsuitable for many applications where rapid cool-down and long cooling durations from a limited size gas supply source are required. Rapid cool-down requires high rate gas flow and a large size orifice, while long cooling durations require low gas flow rates and a small size orifice.
  • cryostats with internal, passive, thermostatic control of variable orifice size have been used as shown in FIG. 1B. These cryostats have the ability to start cool-down with the maximum orifice size, thereby providing high rate gas flow and refrigeration for rapid cool-down. After cool-down is achieved, the orifice size is reduced for minimal gas flow rate and refrigeration necessary for the thermal load.
  • a thermostatic element within the mandrel 5 provides self-regulation of gas flow based upon the temperature in and around the gas plenum chamber 29.
  • the cooling rate is proportional to the mass flow rate of gas through the cryostat.
  • the thermostatic element which can be a gas- filled bellows or a segment of material which contracts or expands based upon temperature, is coupled to a demand-flow needle valve mechanism 19.
  • the bellows As the temperature drops, the bellows is adapted to contract and cause the needle to extend into and partially close the Joule-Thomson orifice 16.
  • the bellows thermostat mechanism 17 can close the needle valve 19 entirely.
  • the bellows expands again and actuates the valve mechanism 19, allowing new coolant flow through the orifice and ultimately to the heat load 15.
  • thermostat bellows mechanism 17 (and similar substitute devices that rely upon expansion and contraction of materials, such as certain plastics) are inherently subject to large performance tolerances. This can result in instabilities and fluctuations in the critical on-off temperature point for the needle valve. Therefore, such cryostats have been found to be non- proportional in their gas flow regulation over the expected full range of operation.
  • cryostat will react differently using different cryogens. Thus, the system performance will be dependent upon the specific cryogen in use during any single operation. If a substitute coolant is used in place of that for which the thermal contraction link is designed, the cryostat will seek the design set temperature and may repeatedly fail.
  • thermophonics a type of thermal noise, known as thermophonics
  • any of these exemplary conditional aspects can result in a premature closing or undesired variations in the needle valve positioning and gas flow rate. This forces a manufacturing design of a multiplicity of Joule-Thomson cryostat components tailored to both heat load factors and coolant parameters.
  • cryostats which can use the sensed temperature of the thermal load, and not just the gas plenum chamber temperature, to adjust the gas expansion valve orifice size setting from maximum opening during cool-down to a reduced minimal opening for sustained cooling of the thermal load.
  • cryostats provide stable, time-averaged, proportional control of the gas expansion valve orifice size for stable gas flow and, therefore, stable refrigeration rate and temperature control.
  • this control should be able to adjust to changing heat load and input pressure conditions, as well as changing thermal environments in a continuous, gradual and non- abrupt manner, which maintains a stable cold temperature.
  • this control should be able to work with multiple coolant gases and provide a stable cold temperature and optimal performance.
  • cryostats that minimizes susceptibility to temperature fluctuations caused by outside environmental effects, such as inertial accelerations, or to internal thermal waves, or to pressure variations within the plenum chamber.
  • the present invention addresses these needs.
  • the present invention is adaptable to a configuration of a cryostat of the type shown in FIG. 1A.
  • FIG. 2A shows the invention as incorporated into such a Joule-Thomson cryostat.
  • the invention is contained within the cold finger 7 of the vacuum dewar container 9 of like manner to the prior art of FIG. 1A.
  • a mandrel cap member 21 seals a mandrel chamber 23.
  • the cap member 21 comprises an encapsulated thermal foam insulation 25, such as polyurethane, to prevent thermal leakage from the chamber 23.
  • the coolant plenum chamber 29 houses a fixedly mounted bellows spring 31.
  • a low mass, high spring constant device is used for the bellows spring 31.
  • an electrical feedthrough connector 35 In the preferred embodiment, this is a glass-to-metal feedthrough connector 35.
  • the feedthrough connector 35 has an electrical lead 55 terminating externally of the mandrel cap 21.
  • a bellows spring actuator mechanism is terminated at a first end 39 in the feedthrough connector 35.
  • the bellows spring actuator comprises a first section, which, in the preferred embodiment, is a biometal wire rod 41.
  • the rod 41 extends through the length of the mandrel cap 21 toward the sheath tubing 27 and is coupled at an electrical return junction 43 to a wire rod 45, in the preferred embodiment a steel wire rod. Note that with a relatively sturdy rod 45, the sheath 27 may be eliminated.
  • An electrical return wire 55' coupled to the junction 43 also leads externally of the mandrel cap 21.
  • the biometal rod 41 acts as a transducer.
  • the biometal wire rod 41 is a type of titanium-nickel shape memory alloy which contracts during heating when an electrical current is passed through it (known in the art as martensitic-austensitic phase transitioning). Either a small proportional direct current or a pulse-width modulated electric current may be provided through the rod 41 via the pair of electrical leads 55, 55'.
  • the rod 41 thus acts as a miniature transducer for translating motion, using the attached steel wire rod 45, to a needle valve 19 in the coolant plenum chamber 29.
  • biometal could be a solid-state electromagnetic device, such as a solenoid or magnetostrictive alloy, or another solid-state electromechanical device, such as a piezoelectric transducer.
  • a solid-state electromagnetic device such as a solenoid or magnetostrictive alloy
  • another solid-state electromechanical device such as a piezoelectric transducer.
  • the application of the cryostat may dictate which alternative is most appropriate.
  • electrical current is applied to the wire rod 41 through feedthrough connector 35 (FIG. 3). Current is also supplied by wires 62 and 63 to a heating element 64.
  • the steel wire rod 45 connected to the biometal wire rod 41 at the electrical return junction 43, runs through the sheath tubing 27 to a bellows compression plate 47 connected to the movable end of the bellows spring 31.
  • the bellows spring 31 is connected to a needle valve mechanism 19 within the coolant plenum chamber 29 via bellows pressure plate 47.
  • the combination of spring 31 and pressure plate connected through the steel wire rod 45 to the biometal rod 41 forms a valve actuator device.
  • the needle valve mechanism 19 and connection bellows spring 31 is similar or identical to that recognized by a person skilled in the art as exemplified in FIG. 1B.
  • a thermal sensor 51 is mounted on, or adjacent, a thermal load mounting platform 15' (which may be integral with the particular load).
  • a silicon diode temperature sensor 51 is fixedly mounted on the heat load platform 15' in close proximity to the load 15.
  • a commercially available sensor such as the IN914 diode manufactured by Texas Instruments is suitable for use in the present invention.
  • Transistor-type sensors may alternatively be employed in the invention.
  • the sensor 51 is mounted so as to be sensitive to the ambient temperature of the load environment rather than the temperature within the plenum chamber 29.
  • FIG. 3 the invention is represented in a schematic diagram to assist understanding of its operation.
  • the heat load 15 that requires temperature control for example, a missile infrared detector or focal plane array, is fixedly mounted on a thermal load platform 15'.
  • the platform 15' is in turn located adjacent to the cryostat near an orifice 16 as shown in FIG. 2A.
  • a servo-controller actuator 53 is coupled by electrical leads 55, 55'(return) to the bellows spring actuator 57 and thermal sensor 51.
  • Qx there are various sources of heat comprising the load.
  • the load 15 and its platform 15', Qfpa and other load environment heat contributors are shown as Qrad, Qcond and even Qvalve, representing heat generated from the valve actuator itself Heat to be extracted by the cryostat is shown a -Qcryo.
  • the temperature sensor 51 provides feedback from the load 15, 15' environment to a servo-controller 53 of the valve control actuator 57.
  • the operational parameters of the servo-controller 53 are designed to control the dimensional length of the biometal rod 41 based upon the sensed temperature.
  • Servo-controller actuator 53 current being coupled to the biometal wire rod 41 by the electrical leads 55, 55' drives the transducer action of the biometal wire rod 41.
  • the steel wire rod 45 attached to the biometal wire rod 41 controls the bellows spring 31 and, thus, the Joule-Thomson orifice of the needle valve 19 and, therefore, the flow of the coolant to the load 15.
  • the method of operation is depicted in the block diagram designated FIG. 4.
  • the servo-controller 53 of the valve control actuator 57 is activated at the time when the coolant gas is input through the gas inlet fitting 1 into the heat exchanger 3.
  • the current to the biometal rod 41 is turned on to reach a predetermined temperature which is just below the phase transition temperature of the preselected biometal material used in rod 41.
  • the needle valve 19 is normally wide open to maximize gas flow and refrigeration effectiveness.
  • the temperature sensor 51 provides a temperature error feedback signal to the servo-controller 59 of the valve control actuator 57, as shown by reference numeral 105.
  • the servo-controller 59 begins to generate an additional current into the biometal wire rod 41 via electrical lead 55 and feedthrough connector 35.
  • the biometal material contracts. This contraction, transmitted through the steel wire rod 37 and bellows pressure plate 47 throttles the coupled needle into the valve orifice and reduces gas flow and, therefore, the Joule-Thomson cryostat refrigeration effect.
  • the gas flow cut back continues until the load temperature rises above the reference level which is detected by the thermal sensor 51.
  • the current to the biometal wire 41 is cut back, causing the reverse reaction and opening the orifice of the needle valve 19 to produce more refrigeration.
  • the temperature may oscillate but only until the temperature error signal is properly nulled to zero when the feedback through the valve control actuator 57 has adjusted the needle valve 19 orifice to a size where the refrigeration rate matches the thermal load within the desired reference temperature range.
  • FIG. 5 shows an alternative embodiment of the valve control actuator 57 to include a fine servo-controller 61 coupled to the temperature sensor 51 by electrical lead pair 56. Also shown, the fine servo-controller element 61 drives a heating element 64 located inside the cold end of the cryostat chamber 23 or, as shown on FIG. 5, is alternatively mounted near the heat load 15. The function of the second fine servo-controller element 61 is to add any additional necessary heat to maintain the load temperature within a finer tolerance reference temperature range for the specific load.
  • FIG. 6 the operation of the alternative embodiment of FIG. 5 is depicted in the block diagram of FIG. 6.
  • a secondary servo loop with feedback uses small amounts of electrical heater power added to the thermal load to maintain the temperature constant within tighter tolerances.
  • This invention is also capable of operating in the saturated to near-saturated operating mode. For example, by using a servo-control reference temperature slightly above the liquid cryogen boiling temperature, but converting the servo-controller from a null search mode to a mode that delivers a fixed predetermined output current when the threshold temperature is reached, the cryostat would be made to operate with the orifice reduced but fixed, during sustained cooling, to produce a slight excess of liquid cryogen.
  • the invention is useful in Joule-Thomson cryo-systems which provide fast cool down and long duration cooling from minimal size and weight gas supply systems, for example, in missile systems.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Temperature (AREA)
  • Temperature-Responsive Valves (AREA)
EP96108475A 1995-06-06 1996-05-28 Cryostat Joule-Thomson Withdrawn EP0747644A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US46916395A 1995-06-06 1995-06-06
US469163 1995-06-06

Publications (2)

Publication Number Publication Date
EP0747644A2 true EP0747644A2 (fr) 1996-12-11
EP0747644A3 EP0747644A3 (fr) 1999-01-20

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EP96108475A Withdrawn EP0747644A3 (fr) 1995-06-06 1996-05-28 Cryostat Joule-Thomson

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EP (1) EP0747644A3 (fr)
JP (1) JPH0932965A (fr)
KR (1) KR100200255B1 (fr)
AU (1) AU5238396A (fr)
CA (1) CA2178124C (fr)
IL (1) IL118511A0 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999023426A1 (fr) * 1997-10-30 1999-05-14 Raytheon Company Cryostat thermo-elastique reactif
WO2007017866A1 (fr) * 2005-08-11 2007-02-15 Rafael Advanced Defense Systems Ltd. Réduction du temps de stabilisation de la température d’un détecteur ir dans le procédé de refroidissement cryogénique joule-thomson
WO2008047357A2 (fr) 2006-10-16 2008-04-24 Rafael-Armament Development Authority Ltd. Soupape à commande de température destinée à réguler le flux de gaz de refroidissement
WO2009130137A1 (fr) * 2008-04-25 2009-10-29 Thales Systeme optronique ir a maintenance predictive a partir d'une derive brutale
WO2012049673A2 (fr) * 2010-10-11 2012-04-19 Rafael Advanced Defense Systems Ltd. Système de refroidissement de joule-thompson régulé qui comprend une boucle de régulation fermée active pour l'augmentation de la fiabilité et la prévention d'une surchauffe instantanée
CN110195995A (zh) * 2019-05-15 2019-09-03 中国电子科技集团公司第十一研究所 制冷器的自调机构及其装配方法、自调式j-t制冷器
CN112730505A (zh) * 2020-12-18 2021-04-30 上海交通大学 用于低温流体节流和定量测量的可视化实验舱

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TW200636198A (en) * 2004-12-30 2006-10-16 Twister Bv Throttling valve and method for enlarging liquid droplet sizes in a fluid stream flowing therethrough
US9765995B2 (en) * 2012-06-27 2017-09-19 Raytheon Company Cryocoolers with electronic cryostat flow controllers and related system and method

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0005048A1 (fr) * 1978-04-13 1979-10-31 Air Products And Chemicals, Inc. Cryostat
FR2642510A1 (fr) * 1989-02-02 1990-08-03 Albagnac Rene Regulateur de debit de gaz pour refroidisseur a effet joule-thomson
GB2247517A (en) * 1990-08-07 1992-03-04 Hymatic Eng Co Ltd Cryogenic cooling apparatus
EP0582817A1 (fr) * 1992-08-13 1994-02-16 BODENSEEWERK GERÄTETECHNIK GmbH Système frigorifique pour refroidissement d'un objet à des basses températures par un refroidisseur Joule Thomson

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62182558A (ja) * 1986-02-05 1987-08-10 日本電気株式会社 ジユ−ルトムソン冷却装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0005048A1 (fr) * 1978-04-13 1979-10-31 Air Products And Chemicals, Inc. Cryostat
FR2642510A1 (fr) * 1989-02-02 1990-08-03 Albagnac Rene Regulateur de debit de gaz pour refroidisseur a effet joule-thomson
GB2247517A (en) * 1990-08-07 1992-03-04 Hymatic Eng Co Ltd Cryogenic cooling apparatus
EP0582817A1 (fr) * 1992-08-13 1994-02-16 BODENSEEWERK GERÄTETECHNIK GmbH Système frigorifique pour refroidissement d'un objet à des basses températures par un refroidisseur Joule Thomson

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999023426A1 (fr) * 1997-10-30 1999-05-14 Raytheon Company Cryostat thermo-elastique reactif
WO2007017866A1 (fr) * 2005-08-11 2007-02-15 Rafael Advanced Defense Systems Ltd. Réduction du temps de stabilisation de la température d’un détecteur ir dans le procédé de refroidissement cryogénique joule-thomson
WO2008047357A2 (fr) 2006-10-16 2008-04-24 Rafael-Armament Development Authority Ltd. Soupape à commande de température destinée à réguler le flux de gaz de refroidissement
WO2009130137A1 (fr) * 2008-04-25 2009-10-29 Thales Systeme optronique ir a maintenance predictive a partir d'une derive brutale
FR2930677A1 (fr) * 2008-04-25 2009-10-30 Thales Sa Systeme optronique ir a maintenance predictive a partir d'une derive brutale
US9010134B2 (en) 2008-04-25 2015-04-21 Thales Optronic infrared system with predictive maintenance following a sudden drift
WO2012049673A2 (fr) * 2010-10-11 2012-04-19 Rafael Advanced Defense Systems Ltd. Système de refroidissement de joule-thompson régulé qui comprend une boucle de régulation fermée active pour l'augmentation de la fiabilité et la prévention d'une surchauffe instantanée
WO2012049673A3 (fr) * 2010-10-11 2012-07-12 Rafael Advanced Defense Systems Ltd. Système de refroidissement de joule-thompson régulé qui comprend une boucle de régulation fermée active pour l'augmentation de la fiabilité et la prévention d'une surchauffe instantanée
CN110195995A (zh) * 2019-05-15 2019-09-03 中国电子科技集团公司第十一研究所 制冷器的自调机构及其装配方法、自调式j-t制冷器
CN112730505A (zh) * 2020-12-18 2021-04-30 上海交通大学 用于低温流体节流和定量测量的可视化实验舱

Also Published As

Publication number Publication date
KR100200255B1 (ko) 1999-06-15
AU5238396A (en) 1996-12-19
CA2178124C (fr) 2002-05-14
JPH0932965A (ja) 1997-02-07
CA2178124A1 (fr) 1996-12-07
IL118511A0 (en) 1996-09-12
EP0747644A3 (fr) 1999-01-20

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