EP0432583B1 - Dispositif de refroidissement - Google Patents

Dispositif de refroidissement Download PDF

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Publication number
EP0432583B1
EP0432583B1 EP90122816A EP90122816A EP0432583B1 EP 0432583 B1 EP0432583 B1 EP 0432583B1 EP 90122816 A EP90122816 A EP 90122816A EP 90122816 A EP90122816 A EP 90122816A EP 0432583 B1 EP0432583 B1 EP 0432583B1
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EP
European Patent Office
Prior art keywords
cooler
gas
heat exchanger
jacket
cooling device
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
Application number
EP90122816A
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German (de)
English (en)
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EP0432583A1 (fr
Inventor
Uwe Dr. Hingst
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Bodenseewerk Geratetechnik GmbH
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Bodenseewerk Geratetechnik GmbH
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Publication of EP0432583A1 publication Critical patent/EP0432583A1/fr
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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
    • F25B9/02—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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
    • 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
    • F25B2309/023—Gas cycle refrigeration machines using the Joule-Thompson effect with two stage expansion
    • 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/12—Inflammable refrigerants

Definitions

  • the expansion cooler and the counterflow cooler are wound together on a carrier which is surrounded by a housing.
  • the second gas which flows through the countercurrent cooler under high pressure, has a high Joule-Thomson effect and can be selected, for example, from argon, methane or trifluoromethane. It is therefore liquefied in the housing and serves to cool the first gas below the inversion temperature.
  • the whole arrangement is located in an outer jacket, on the closed side of which an infrared detector is arranged on the outside.
  • the expansion outlet of the expansion cooler protruding from the housing and through which, for example, nitrogen flows at a lower pressure, is directed towards the closed side of the outer jacket.
  • GB-A-1 238 911 also discloses a cooling device in which cooling is achieved by the expansion of a gas under pressure through a nozzle.
  • the gas must be at a temperature below its inversion temperature before the expansion.
  • the cooling device according to GB-A-1 238 911 has two coolers.
  • a first cooler a first gas is passed from a compressed gas source in gaseous form via a first path of a countercurrent heat exchanger, expanded through the nozzle and returned in countercurrent via a second path of the heat exchanger. This cools the leading, pressurized gas.
  • the second cooler pre-cools the first gas before it reaches the countercurrent heat exchanger of the first cooler.
  • the second cooler receives one Liquid under pressure, which is sprayed through a nozzle into a chamber. The liquid evaporates, which achieves the cooling effect of the second cooler.
  • the first cooler cools an object in the form of an infrared detector.
  • DE-A1-36 42 683 describes a cryostat based on the Joule-Thomson effect for cooling an infrared detector.
  • a counterflow heat exchanger sits with a flow line in a Dewar vessel. The flow line ends in an expansion nozzle.
  • the infrared detector sits on the front wall of the inside of the Dewar flask.
  • a heat-insulating layer is arranged between the Dewar vessel and a base.
  • an inlet end of the flow line is cooled by Peltier elements.
  • DE-A-1 501 715 shows a device for liquefying gases with two expansion coolers, a first of which is operated with hydrogen and a second with air or nitrogen.
  • Both expansion coolers are designed as Joule-Thomson coolers, ie they contain a countercurrent heat exchanger in which the respective expanded and cooled gas exchanges heat with the leading gas.
  • the liquid nitrogen or the liquid air obtained by the second Joule-Thomson cooler serve to pre-cool the hydrogen in the first Joule-Thomson cooler.
  • the hydrogen is cooled to below its inversion temperature.
  • the nitrogen can only be cooled down to its boiling point by the Joule-Thomson cooler.
  • EP-A-0 271 989 describes the use of a coolant in the form of a mixture of nitrogen, argon or neon with methane, ethane or propane with the addition of combustion-inhibiting materials such as bromotrifluoromethane in a conventional single-stage Joule-Thomson cooler.
  • DE-A-3 337 194, DE-A-3 337 195, GB-A-2 119 071 and EP-A-0 234 644 show the use of single-stage Joule-Thomson coolers for cooling electronic or opto- electronic components.
  • German patent application P 39 25 942.0 it is proposed in the (not prepublished) German patent application P 39 25 942.0 to arrange the viewfinder on a support which is aligned with the axis of the gyro rotor and thus the optical axis of the imaging optical system, so that also a "squint" of the viewfinder, the plane of the flat detector is always perpendicular to this optical axis.
  • Joule-Thomson coolers usually used for cooling detectors a countercurrent heat exchanger is provided, via which the relaxed and cooled gas flows back, the inflowing gas being pre-cooled by the returning gas.
  • the expanded gas must be used as completely as possible for the pre-cooling. Avoid gas and heat losses. This can be achieved if a detector is arranged stationary in a Dewar vessel. However, difficulties arise when the detector is arranged on a movable carrier.
  • the invention has for its object to improve the cooling performance of a cooler with substantially the same total gas consumption.
  • the invention is further based on the object of providing a cooler by means of which an object can be cooled without it being necessary to arrange this object in a stationary manner in a Dewar vessel.
  • the invention is particularly based on the object of cooling a linear or flat detector in a gyro-stabilized viewfinder, in which the detector can be aligned according to the optical axis of the "squinting" optical system.
  • the gas cooled by the first cooler is precooled exclusively by means of the second cooler.
  • a gas can be selected that provides a high cooling effect but may have a boiling point that is too high for cooling the detector.
  • the first cooler works with a gas with a low boiling point, which after relaxation and cooling is directed only to the object to be cooled and its surroundings and does not need to perform a pre-cooling function. It can be shown that the total gas consumption required for a given cooling capacity is first and second Gas is not, or only slightly, greater than the gas consumption of a single Joule-Thomson cooler.
  • the first gas is advantageously argon.
  • the second gas can be methane. Methane provides good cooling performance in a Joule-Thomson cooler, which is about five times higher in weight than the cooling performance achievable with argon, but has a relatively high boiling point of 118 K.
  • the second gas can also be freon (CF4). Freon also delivers high cooling performance at a boiling point of 145 K at atmospheric pressure.
  • the object can face the relaxation outlet of the first cooler can be pivoted and preferably an infrared detector of a viewfinder.
  • An advantageous constructive solution consists in that a jacket which is closed at its end on the object side is provided, in the jacket the heat exchanger of the first cooler is arranged on the object side, in the jacket on the side of the heat exchanger of the first cooler facing away from the object, the countercurrent heat exchanger of the second Cooler is arranged, from the outlet end of the countercurrent heat exchanger, a second gas-carrying line is passed through the heat exchanger of the first cooler, which ends between this heat exchanger and the closed end of the jacket in the expansion opening of the second cooler, and from the outlet end the heat exchanger of the first cooler starts a line carrying the first gas, which is passed through the closed end of the jacket and ends in the expansion outlet of the first cooler.
  • the jacket can have a smaller diameter in the area of the heat exchanger of the first cooler than in the area of the counterflow heat exchanger of the second cooler.
  • the line from the heat exchanger of the first cooler to the expansion outlet of the first cooler can be thermally insulated to the object.
  • a conventional Joule-Thomson cooler 10 is shown schematically in FIG.
  • Pressurized gas namely argon
  • the pressurized gas flows from a pressurized bottle 12 via an inlet 14 to the flow path 16 of a countercurrent heat exchanger 18.
  • the pressurized gas exits through a throttle or nozzle 20 into a relaxation space 22.
  • the gas is cooled.
  • the expanded and cooled gas flows back from the expansion space 22 via the return path 24 of the countercurrent heat exchanger 18 and exits at an outlet 26.
  • the inflowing compressed gas is pre-cooled by the returning gas.
  • an infrared detector is designated, which is to be cooled by the Joule-Thomson cooler 10.
  • the infrared detector 28 sits on the inner wall 30 of a Dewar vessel (not shown) surrounding the Joule-Thomson cooler 10.
  • the compressed gas is at the inlet 14 at a temperature of approximately 350 K at a pressure of 500 bar. That is the point "b" in the diagram.
  • the pressure remains essentially constant along the flow path 16 of the countercurrent heat exchanger 18, but the temperature drops due to the pre-cooling by means of the back-flowing gas.
  • the state thus changes to state "c", which prevails spatially immediately in front of the nozzle 20 along a curve 32 of constant pressure.
  • the gas is released at the nozzle 20.
  • the state changes in the diagram along a curve 33 of constant enthalpy up to point "d".
  • the point "d" lies on the wet steam line 34.
  • the gas is partially condensed so that a mixture of gas and steam occurs.
  • the temperature remains constant.
  • a cooling device with two coolers 40 and 42 is shown schematically in FIG.
  • the first cooler 40 is operated with argon from an argon compressed gas container 44.
  • the argon in the compressed gas container 44 is at ambient temperature and is under a pressure of 200 to 500 bar.
  • the argon is conducted via a valve 46 and a line 48 which is running straight through the second cooler 42 to a flow path 50 of a heat exchanger 51 of the cooler 40.
  • the first cooler 40 is an expansion cooler with a throttle 52.
  • the throttle 52 is connected to the outlet of the flow path 50 via a high-pressure line 54.
  • the high pressure line 54 is provided with thermal insulation 56.
  • the second cooler 42 is operated with methane CH4 from a methane pressure gas container 58.
  • the methane in the compressed gas container is also at ambient temperature and is under a pressure of 200 to 350 bar.
  • the methane is conducted via a valve to the inlet 62 of a flow path 64 of a countercurrent heat exchanger 66 of the second cooler 42. From the outlet 68 of the flow path 64 of the countercurrent heat exchanger 66, a line 70 goes straight through the second cooler 40 to a throttle 72.
  • the throttle 72 is located at the end of the first cooler 40 facing away from the second cooler 42 the high pressure methane. The methane relaxes and cools down.
  • the relaxed and cooled methane now flows through a return path 74 of the heat exchanger 51 of the first cooler 40 in counterflow to the leading argon.
  • the argon is thus pre-cooled by the relaxed methane wet steam, not by the relaxed argon.
  • the expanded methane gas then flows through a return path 76 of the countercurrent heat exchanger 66 of the second cooler 42.
  • the leading, high-pressure methane is pre-cooled by the expanded and cooled methane.
  • the methane exits the return path 76 at an outlet 78.
  • the outflowing argon is directed in a beam onto an infrared detector 80, which is arranged in a movable carrier 82.
  • the argon then emerges from the carrier 82 through an opening 84.
  • the two coolers 40 and 42 are enclosed by a jacket 86, which is closed on the object side by an end wall 88.
  • the heat-insulated high-pressure line 54 is led through the end wall 88.
  • the methane is cooled down to the boiling point of the methane by the second cooler 42 and the throttle 72 in a Joule-Thomson process. It has already been mentioned above that methane has a much higher cooling capacity than argon. However, the boiling point of the methane at 118 K cannot be undercut. Liquid methane forms in the jacket 86, as indicated at 90. The heat exchange with the methane in the heat exchanger 51 pre-cools the argon to the boiling point of the methane. The state of argon therefore moves along curve 32 of constant pressure to point "f". The state occurs when the argon is expanded at the throttle 52 along curve 92 constant enthalpy to point "g" on wet steam line 34. A jet emerges at throttle 52 with a mixture of gaseous and liquid argon at a temperature of 87 K, the boiling point of argon.
  • this argon does not need to pre-cool the leading, pressurized argon. It evaporates, and the point representing the state moves along the wet steam line to the right to point "d” ". Then the argon heats up.
  • the object ie the detector 80
  • the argon has cooled to the boiling temperature of the argon, ie 87 K
  • the warming argon naturally no longer absorbs heat from the object, but the still very cold argon can still be used to cool the surroundings of the detector 80 and its feed lines and thus to reduce the heat supply to the detector 80 Cooling capacity is determined by the difference between the enthalpies in point "g" and in point "d” ".
  • tetrafluorocarbon CF4 can also be used as the cooling gas. However, its boiling point is somewhat higher, namely 145 K, as shown in FIG. 1.
  • FIG. 3 shows a constructive embodiment of the cooling device.
  • the structure of the cooling device largely corresponds to the schematic illustration of FIG. 2.
  • Corresponding parts are provided with the same reference numerals as in Fig.2.
  • a base 94 is attachable to a structure with a flange 96. Pipelines 98 and 100 for argon and methane are led through the base 94 and are led from the compressed gas containers 44 and 58 to the coolers 40 and 42, respectively.
  • a sleeve 102 is held in the base 94 with a foot 104. The sleeve 102 sits coaxially in the jacket 86, which can form the inner wall of a Dewar vessel but can also be part of a simple, heat-insulating housing.
  • the jacket 86 has a section 106 of larger diameter at its open end and a section 108 of smaller diameter at its end closed by the end wall 88.
  • An annular space 110 is formed between the section 106 of the jacket and the sleeve 102.
  • the flow path 64 of the countercurrent heat exchanger 66 is located in the annular space 110.
  • the flow path 64 of the counterflow heat exchanger 66 is formed by a tube 112 which extends helically around the sleeve 102.
  • the tube 112 is provided with fins 114 to improve heat exchange.
  • the return path 76 of the counterflow heat exchanger 66 is formed by the annular space 110.
  • the relaxed methane flows out of this annulus.
  • the tube 112 ends in a straight line 70 which extends centrally through the section 108 of the jacket 86 and ends close to the end wall 88. At the end, the line 70 forms a nozzle which forms the throttle 72 (FIG. 2).
  • the pipe 112 is connected to the pipe 100, as indicated by the broken line 116 in FIG.
  • the pipeline 98 is connected to the line 48.
  • the line 42 extends straight inside the sleeve 102.
  • the connection between the pipeline 98 and the line 48 is indicated in FIG. 3 by a dashed line 118.
  • the flow path 50 of the argon connected to the line 48 is formed by a tube 120.
  • the tube 120 is arranged helically within the section 108 of the jacket 86 around the straight line 70.
  • the tube 120 is also provided with fins 122 to improve heat exchange.
  • In the section 108 there is a sleeve 124 which surrounds the helix of the tube 120 and is closed off by the end wall 88.
  • the tube 120 is sealingly guided through the end wall 88 with a seal 126 and merges into the heat-insulated high-pressure tube 54.
  • the high-pressure pipe 54 ends in a nozzle which forms the DRossel 52 (FIG. 2).
  • the return path 74 of the first cooler 40 is formed by the interior of the sleeve 124.
  • the methane flows over the argon-carrying pipe 120 in heat exchange therewith. Then the relaxed methane flows, as indicated by arrow 128, into the annular space 110 and then cools the tube 112 with the leading methane. In section 108 in heat exchanger 51, the methane is present as wet steam, partly liquid, partly gaseous at the boiling point of the methane. At the transition from section 108 to section 106 with the annular space 110, however, the methane is already gaseous again.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)

Claims (11)

  1. Dispositif de refroidissement d'un objet, comprenant
    (a) un premier réfrigérant (40) destiné à refroidir l'objet (80), dans lequel le premier réfrigérant (40) est relié, sur le côté entrée, à une alimentation pour un premier gaz sous pression prérefroidi au-dessous de son point d'inversion et à une température d'ébullition relativement basse et à puissance de refroidissement faible, et présente une sortie de détente (52) par laquelle le premier gaz est détendu sous refroidissement,
    (b) un second réfrigérant (42) relié, sur le côté entrée, à une alimentation pour un second gaz à température d'ébullition plus élevée par rapport au premier gaz et à puissance de refroidissement plus élevée afin de prérefroidir le premier gaz, dans lequel
    (c) le second réfrigérant (42) est un réfrigérant Joule-Thomson muni d'une sortie de détente (72) par laquelle le second gaz sous pression est détendu sous refroidissement, et muni d'un échangeur thermique à contrecourant (66) intercalé en avant de la sortie de détente (72) et par lequel le second gaz alimenté est susceptible d'être prérefroidi par le second gaz refroidi détendu, et
    (d) le premier réfrigérant (40) est un réfrigérant d'expansion muni d'un échangeur thermique (51) intercalé en avant de la sortie de détente (52) dans lequel le premier gaz sous pression n'est en échange thermique qu'avec le second gaz détendu et refroidi,
       caractérisé par le fait que
    (e) le premier réfrigérant (40) est disposé en aval du second réfrigérant (42), et la sortie de détente (72) du second réfrigérant (42) est disposée sur l'extrémité du premier réfrigérant (40), qui est opposée au second réfrigérant (42) de sorte que le second gaz détendu sortant de la sortie de détente (72) ne refroidit d'abord dans le premier réfrigérant (40) que le premier gaz sous pression dans le coutrecourant, et ensuite dans le second réfrigérant (42) que le second gaz sous pression dans le contrecourant, et
    (f) la sortie de détente (52) du premier réfrigérant (40) est dirigée directement contre l'objet à refroidir (80).
  2. Dispositif de refroidissement selon la revendication 1, caractérisé par le fait que le premier gaz est de l'argone.
  3. Dispositif de refroidissement selon la revendication 1 ou 2, caractérisé par le fait que le second gaz est du méthane.
  4. Dispositif de refroidissement selon la revendication 1 ou 2, caractérisé par le fait que le second gaz est du fréon.
  5. Dispositif de refroidissement selon l'une des revendications 1 à 4, caractérisé par le fait que l'objet (80) est pivotable par rapport à la sortie de détente (52) du premier réfrigérant (40).
  6. Dispositif de refroidissement selon la revendication 5, caractérisé par le fait que l'objet (80) est un détecteur infrarouge d'un chercheur.
  7. Dispositif de refroidissement selon l'une des revendications 1 à 6, caractérisé par le fait que
    (a) on a prévu une chemise (86) fermée sur l'extrémité du côté objet,
    (b) l'échangeur thermique (51) du premier réfrigérant (40) est disposé dans la chemise (86) du côté objet,
    (c) l'échangeur thermique à contrecourant (66) du second réfrigérant (42) est disposé dans la chemise (86) sur le côté de l'échangeur thermique (51) du premier réfrigérant (40), qui est opposé à l'objet,
    (d) une conduite (70) conduisant le second gaz est passée depuis l'extrémité du côté sortie de l'échangeur thermique à contrecourant (66) à travers l'échangeur thermique (51) du premier réfrigérant (40), et débouche entre cet échangeur thermique (51) et l'extrémité fermée de la chemise (86) dans la sortie de détente (72) du second réfrigérant (42), et
    (e) une conduite (54) conduisant le premier gaz part de l'extrémité du côté entrée de l'échangeur thermique (51) du premier réfrigérant (40), et passe à travers l'extrémité fermée de la chemise (86) et débouche dans la sortie de détente (52) du premier réfrigérant (40).
  8. Dispositif de refroidissement selon la revendication 7, caractérisé par le fait que la chemise (86) a dans le domaine de l'échangeur thermique (51) du premier réfrigérant (40), un diamètre plus petit que dans le domaine de l'échangeur thermique à contrecourant (66) du second réfrigérant (42).
  9. Dispositif de refroidissement selon la revendication 8, caractérisé par le fait que
    (a) un manchon (102) est disposé dans la section (106) avec le diamètre plus grand de la chemise (86), concentriquement à la chemise, manchon qui est fermé sur le côté de l'extrémité ouverte de la chemise (86) et forme un espace annulaire (110) avec la chemise (86),
    (b) la voie de marche avant (64) de l'échangeur thermique à contrecourant (66) est formée par un tuyau (112) hélicoidal muni de nervures (114) et disposé dans l'espace annulaire (110) autour du manchon (102),
    (c) la voie de retour (76) de l'échangeur thermique à contrecourant (66) est formée par l'espace annulaire (110).
  10. Dispositif de refroidissement selon la revendication 9, caractérisé par le fait que
    (d) la conduite (42) étroite conduisant vers le côté entrée de la voie de marche avant (50) de l'échangeur thermique (51) du premier réfrigérant (40) est guidée à l'intérieur du manchon,
    (e) la voie de marche avant (50) de l'échangeur thermique (51) du premier réfrigérant (40) est formée par un tuyau (120) hélicoidal muni de nervures (122) et disposé à l'intérieur de la section (108) à petit diamètre de la chemise (86), et
    (f) la conduite étroite conduisant le second gaz sous pression, est guidée centralement par l'hélice formée par le tuyau (120) et forme la sortie de détente (72) sur son extrémité étroitement devant une paroi frontale (88) fermant la chemise (86).
  11. Dispositif de refroidissement selon la revendication 10, caractérisé par le fait que l'extrémité du côté sortie du tuyau (120) passe à une conduite à haute pression (54) à isolation thermique guidée à travers la paroi frontale (88), guidée vers l'objet et débouchant dans la sortie de détente (52) du premier réfrigérant (40).
EP90122816A 1989-12-14 1990-11-29 Dispositif de refroidissement Expired - Lifetime EP0432583B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3941314A DE3941314A1 (de) 1989-12-14 1989-12-14 Kuehlvorrichtung
DE3941314 1989-12-14

Publications (2)

Publication Number Publication Date
EP0432583A1 EP0432583A1 (fr) 1991-06-19
EP0432583B1 true EP0432583B1 (fr) 1993-10-20

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EP90122816A Expired - Lifetime EP0432583B1 (fr) 1989-12-14 1990-11-29 Dispositif de refroidissement

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US (1) US5150579A (fr)
EP (1) EP0432583B1 (fr)
DE (2) DE3941314A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004042398A1 (de) * 2004-09-02 2006-03-23 Diehl Bgt Defence Gmbh & Co. Kg Kühlvorrichtung
EP1953478A2 (fr) 2007-02-01 2008-08-06 Diehl BGT Defence GmbH & Co.KG Procédé destiné au refroidissement d'un détecteur
DE102007004999A1 (de) 2007-02-01 2008-08-07 Diehl Bgt Defence Gmbh & Co. Kg Verfahren zur Kühlung eines Detektors

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DE3941314A1 (de) * 1989-12-14 1991-06-20 Bodenseewerk Geraetetech Kuehlvorrichtung
DE4135764C1 (fr) * 1991-10-30 1993-02-25 Bodenseewerk Geraetetechnik Gmbh, 7770 Ueberlingen, De
DE4235752A1 (de) * 1992-10-23 1994-04-28 Licentia Gmbh Kryogene Kühlvorrichtung
FR2707375B1 (fr) * 1993-07-05 1995-09-22 Centre Nat Etd Spatiales Procédé d'obtention de très basses températures.
US5551244A (en) * 1994-11-18 1996-09-03 Martin Marietta Corporation Hybrid thermoelectric/Joule-Thomson cryostat for cooling detectors
US6530234B1 (en) 1995-10-12 2003-03-11 Cryogen, Inc. Precooling system for Joule-Thomson probe
US5787715A (en) * 1995-10-12 1998-08-04 Cryogen, Inc. Mixed gas refrigeration method
US5590538A (en) * 1995-11-16 1997-01-07 Lockheed Missiles And Space Company, Inc. Stacked multistage Joule-Thomson cryostat
US5800488A (en) * 1996-07-23 1998-09-01 Endocare, Inc. Cryoprobe with warming feature
US6505629B1 (en) 1996-07-23 2003-01-14 Endocare, Inc. Cryosurgical system with protective warming feature
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DE3941314A1 (de) 1991-06-20
US5150579A (en) 1992-09-29
DE59003155D1 (de) 1993-11-25
EP0432583A1 (fr) 1991-06-19

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