EP3990839B1 - Kryokühler für einen strahlungsdetektor, insbesondere in einem raumfahrzeug - Google Patents

Kryokühler für einen strahlungsdetektor, insbesondere in einem raumfahrzeug Download PDF

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Publication number
EP3990839B1
EP3990839B1 EP20747050.1A EP20747050A EP3990839B1 EP 3990839 B1 EP3990839 B1 EP 3990839B1 EP 20747050 A EP20747050 A EP 20747050A EP 3990839 B1 EP3990839 B1 EP 3990839B1
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EP
European Patent Office
Prior art keywords
heat transfer
transfer fluid
fluid
cold
return valve
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EP20747050.1A
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English (en)
French (fr)
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EP3990839A1 (de
Inventor
James Butterworth
Clément CHASSAING
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Centre National dEtudes Spatiales CNES
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
Centre National dEtudes Spatiales CNES
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/006—Thermal coupling structure or interface
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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

  • the invention relates to the technical field of cryogenic coolers called “cryocoolers”. More particularly, the invention relates to cryocoolers intended to cool radiation detectors or other organs requiring cooling in spacecraft such as for example in satellites or space probes.
  • Stirling or pulsed gas tube type cryogenic coolers are systems filled with gas, called “working gas”, under pressure at a determined value comprising a piston generating a pressure and flow wave in the gas.
  • the pressure and flow wave will be used to generate cold on a cold finger of the system.
  • the cryogenic cooler thus comprises a pressure and flow wave generator, for example a compressor, and a cold finger.
  • the pressure and flow wave generator transmits the pressure and flow wave in the cold finger, which makes it possible to generate cold down to a determined temperature of the order of -200°C or even lower, in a cold zone of the cold finger for cooling the member to be cooled, for example a satellite radiation detector.
  • a solution which consists in positioning each cold zone of each cooler in a closed thermal circuit called a thermal loop in which a heat transfer fluid is circulated between the cold zone and the component to be cooled.
  • a thermal loop in which a heat transfer fluid is circulated between the cold zone and the component to be cooled.
  • it is possible to selectively activate only one thermal loop so that the thermal loop in which the cold zone of the second cooler is positioned remains inactive and no heat input occurs.
  • Each of these thermal loops can comprise an element of the mechanical circulator type which is used to circulate the heat transfer fluid in the loop. Thus, by activating one of these circulators, the thermal loop which contains it is activated.
  • Another way of circulating the heat transfer fluid is to connect the loop to the output of the pressure and flow wave generator by a system of non-return valves so as to straighten the alternating pressure and flow wave in flow. continued.
  • the working gas of the cooler is of the same nature as the heat transfer fluid in the loop, ie the working gas and the heat transfer fluid are combined.
  • the working gas communicates fluidly with the heat transfer fluid. If a pressure and flow wave generator stops operating, the flow of heat transfer fluid in the loop stops and the associated cold zone is thermally insulated.
  • the "so-called hot extraction” extraction of the heat transfer fluid is carried out when the heat transfer fluid is hot from a transfer line connecting the pressure and flow wave generator and the cold zone, then this fluid
  • the coolant is brought into a “counter-current” heat exchanger, then passes through a heat exchanger thermally connected to the cold zone. Once the heat transfer fluid has cooled, it passes through an application exchanger and then rises in the counter-current exchanger to cool the working gas which descends from the transfer line towards the cold zone.
  • US6637211 describes an oscillating wave motor or refrigerator.
  • a heat transfer gas loop communicates fluidly with the working gas in the engine or refrigerator body.
  • At least one fluid diode in the coolant gas loop produces a continuous flow component superimposed on the oscillating flow emanating from the working gas.
  • the dimensions of the gas loop and the location of the fluidic diodes are chosen so as to make the gas loop resonant.
  • the extraction of the working gas to the coolant gas loop can be done near the hot exchanger (hot extraction) or near the cold exchanger (cold extraction) of the engine or the refrigerator.
  • a secondary heat transfer fluid is in thermal contact with an exterior part of the gas loop. According to US6637211 , resonant loops seem to be suitable only for very high frequency pulse tubes or very long loops.
  • WO2018/065458 A1 discloses a cooling device comprising a heat exchanger, a first flow loop connecting a cold sink and the heat exchanger, and a second flow loop connecting a hot sink and the heat exchanger.
  • a first passive one-way valve is disposed on the first flow loop and a second passive one-way valve is disposed on the second flow loop. The flow directions produce a counter flow in the heat exchanger.
  • the hot sink includes a cryogenic magnet coil, and the hot sink is a cold head and a liquid helium tank.
  • the object of the invention is to remedy all or part of the aforementioned drawbacks and in particular to allow a more advantageous extraction of the heat transfer fluid than that described above without the use of a counter-current exchanger and without the geometric and frequency constraints imposed by a resonant system.
  • part of the pressure and flow wave generated by the pressure and flow wave generator of the cooler is extracted at the level of the cold zone, which allows an extraction cold more advantageous than hot extraction.
  • this configuration makes it possible to combine both a thermal link and a thermal disconnection.
  • the configuration can also operate with a lower temperature of the order of 15K for example, which is hardly possible in the configurations of the prior art.
  • this configuration allows easy distribution of the cold power on the application heat exchanger, of the device to be cooled.
  • the heat transfer fluid exchanges directly with the application unlike the document US6637211 cited previously.
  • a heat transfer fluid circuit is used to thermally disconnect the cold finger from the application and thus limit the thermal load from a redundant cooler.
  • the first non-return valve and the second non-return valve are passive non-return valves.
  • bypassive non-return valve is understood to mean a non-return valve whose geometry is fixed and passive and configured to favor the circulation of a fluid in one direction without a moving element.
  • At least one of the two, preferably each non-return valve comprises one or more Tesla diodes in series.
  • Tesla diodes as described in US1329559 , are that they have asymmetrical impedances and therefore the fluid flows passing through are asymmetrical, which allows the fluid to pass, preferentially the gas, in one direction rather than the opposite direction.
  • the use of a Tesla diode is more reliable, particularly in its application in spacecraft and machines because, unlike mechanical valves, the latter do not pose any problems of reliability or failure due to wear of the parts.
  • the first non-return valve is a non-return valve configured to allow the passage of the heat transfer fluid during positive excursions of the pressure and flow wave in the cold zone.
  • the pressure and flow wave generator creates pressure oscillations at a determined frequency in the heat transfer fluid around an average pressure value. There are therefore successive positive and negative pressure excursions with respect to this average pressure.
  • the second non-return valve is a non-return valve configured to allow the passage of the heat transfer fluid during negative excursions of the pressure and flow wave in the cold zone.
  • the application heat exchanger comprises a plurality of inlets associated with a plurality of fluid outlets.
  • the application heat exchanger comprises at least a second fluid inlet, a second fluid outlet, a third fluid inlet and a third fluid outlet.
  • the cold zone comprises at least a first heat exchange zone in which the heat transfer fluid circulates.
  • the cold zone comprises a plurality of heat exchange zones.
  • the cold zone comprises a cold zone heat exchanger integrating the at least one first heat exchange zone of the cold zone.
  • the cold zone comprises a plurality of cold zone heat exchangers.
  • the outlet of the first non-return valve is fluidically connected to the first inlet of the application heat exchanger.
  • the first fluid outlet of the application heat exchanger is fluidically connected to the first heat exchange zone of the cold zone, the first fluid outlet being positioned upstream of the first heat exchange zone of the cold zone in the direction of circulation of the heat transfer fluid.
  • the second fluid inlet of the application heat exchanger is fluidically connected to the first heat exchange zone of the cold zone, the second fluid inlet being positioned downstream of the first heat exchange zone of the cold zone in the direction of circulation of the heat transfer fluid.
  • the second fluid outlet of the application heat exchanger is fluidically connected to the second heat exchange zone of the cold zone, the second fluid outlet being positioned upstream of the second heat exchange zone of the cold zone in the direction of circulation of the heat transfer fluid.
  • the third fluid inlet of the application heat exchanger is fluidically connected to the second heat exchange zone of the cold zone, the third fluid inlet being positioned downstream of the second heat exchange zone of the cold zone in the direction of circulation of the heat transfer fluid.
  • the third fluid outlet of the application heat exchanger is fluidly connected to the second non-return valve, the third fluid outlet of the exchanger being positioned upstream of the second non-return valve. return in the direction of circulation of the heat transfer fluid.
  • the first non-return valve and the second non-return valve are fluidically connected to the cold zone by a direct line.
  • the cooler comprises a plurality of application heat exchangers, for example three, each comprising at least one coolant fluid inlet and a coolant fluid outlet forming a heat exchange zone.
  • the advantage of allowing circulation of the heat transfer fluid in the heat exchange zones of the cold zone and in the application heat exchanger is that the cooling capacity will be optimized compared to a single pass through the heat exchanger. of application heat and in the cold zone.
  • the heat transport efficiency is multiplied by three.
  • the cold zone can comprise more or fewer heat exchange zones (number of exchange zones greater than or equal to 0) in order to optimize the heat exchange.
  • the application heat exchanger will generally have one more heat exchange area than the cold area.
  • the cooler comprises at least a first buffer tank positioned downstream of the first non-return valve in the direction of circulation of the heat transfer fluid, and configured to smooth the pressure and flow wave which has been straightened by the first non-return valve so as to cause a continuous flow of heat transfer fluid to pass through the circuit.
  • the cooler comprises at least a second buffer tank positioned upstream of the second non-return valve in the direction of circulation of the heat transfer fluid, and configured to smooth the pressure and flow wave which has been straightened by the second non-return valve before being reinjected into the cold zone.
  • the pressure of the heat transfer fluid in the first tank is greater than the pressure of the heat transfer fluid in the second buffer tank.
  • the thermal power transported between the cold zone and the application heat exchanger is equal to the mass flow rate of the heat transfer fluid flow multiplied by the specific heat of the heat transfer fluid multiplied by the difference in temperature between the cold zone and the heat exchanger.
  • part of the heat transfer fluid is injected into the first buffer tank.
  • the heat transfer fluid is sucked from the second buffer tank which creates a pressure difference between the two buffer tanks and this pressure difference which will cause the heat transfer fluid to circulate in the circuit.
  • the heat transfer fluid is a gas and preferably helium.
  • At least one of the two buffer tanks is constituted by a part of the heat transfer fluid circuit.
  • the buffer tank can be formed by locally increasing part of the heat transfer fluid circuit.
  • the cryogenic cooler is a cooler of the pulsed gas tube type or of the Stirling type.
  • the term "Stirling engine or cooler” means an external energy engine or cooler.
  • the main fluid is a gas subjected to a cycle comprising four phases: isochoric heating, isothermal expansion, isochoric cooling then isothermal compression.
  • the thermal link between the cold zone and the application heat exchanger can be longer than 0.5 meters and preferably between 1 and 3 meters.
  • the cooler comprises a plurality of application heat exchangers configured to exchange calories with a plurality of devices to be cooled.
  • the cold finger is in fluid communication with said heat transfer fluid circuit.
  • the cold finger is not in fluid communication with said heat transfer fluid circuit and the cooler comprises a small pressure and flow wave generator fluidly connected to the cold end of the heat transfer fluid circuit .
  • the cold finger is not in fluid communication with said heat transfer fluid circuit and the cooler comprises a direct T-shaped bypass fluidically connecting the pressure and flow wave generator and the cold finger.
  • the invention also relates to a spatial assembly comprising at least one radiation detector and a cryogenic cooler according to the invention, the application heat exchanger being configured to cool the radiation detector.
  • the radiation detector can be a detector of infrared radiation, X-ray, gamma ray, microwave radiation, or any other type of electromagnetic or particle radiation.
  • the cryogenic cooler 100 comprises, whatever the embodiment, a pressure and flow wave generator 110, a cold finger 120 comprising a cold zone 121, a circuit 130 of coolant fluid, at least one application heat exchanger 140, 241, 242, configured to exchange calories with a device to be cooled (not shown).
  • the device to be cooled can be an electromagnetic or particle radiation detector configured to be integrated into a satellite or a space probe.
  • the cryogenic cooler 100 comprises a first non-return valve 150 and a second non-return valve 151.
  • the first non-return valve 150 and the second non-return valve 151 are positioned on either side. other of the cold zone 121 in the circuit 130.
  • the first and second non-return valves are passive non-return valves, for example Tesla diodes.
  • the first non-return valve 150 and the second non-return valve 151 are fluidically connected to the cold zone 121 by a direct line 131.
  • the cold finger 120 comprises a cold zone 121 distal to the pressure wave generator 110 and a hot end 122 proximal to the pressure wave generator 110.
  • a pulse tube 123 is arranged around which is positioned a regenerator 124.
  • a transfer line 101 fluidically connects the pressure and flow wave generator 110 to the cold zone 120.
  • the cold zone 121 is positioned substantially between the regenerator 124 and the pulse tube 123.
  • the cold zone is therefore central.
  • the cold zone 121 comprises a first heat exchange zone 125 and a second heat exchange zone 126 in each of which the heat transfer fluid circulates.
  • the cold zone 121 comprises a cold zone heat exchanger integrating the first 125 and the second 126 heat exchange zone of the cold zone 121.
  • the cryogenic cooler 100 comprising a circuit 130 according to a first embodiment.
  • the heat transfer fluid circulates as follows. From a direct line 131 connecting the cold zone 121 with the first and the second non-return valve 150, 151, the fluid circulates towards the first non-return valve 150 which comprises a channel oriented in a preferential direction of circulation so that the fluid flows preferentially in this direction.
  • the fluid reaches a first buffer tank 152 configured to smooth the pressure of the fluid within the circuit 130.
  • the heat transfer fluid goes to a first fluid inlet 141 of the application heat exchanger 140 configured to exchange with the device to chill.
  • the fluid leaves the exchanger 140 through a first outlet 142 and goes to a second buffer tank 153 configured to again smooth the pressure of the fluid leaving the exchanger.
  • the fluid then passes through the second check valve 151, which is configured in the same flow direction as the first check valve 150.
  • the thermal conductance in operation is substantially 0.12W/K.
  • the cryogenic cooler 100 comprising a circuit 130 according to a second embodiment.
  • the heat transfer fluid circulates as follows. From the direct line 131 connecting the cold zone 121 with the first and the second non-return valve 150, 151, the fluid circulates towards the first non-return valve 150 which comprises a channel oriented in a preferential direction of circulation so that the fluid flows preferentially in this direction.
  • the fluid reaches a first buffer tank 152 configured to smooth the pressure of the fluid within the circuit 130.
  • the heat transfer fluid is directed towards the first fluid inlet 141 of the heat exchanger 140 configured to exchange with the device to be cooled.
  • the fluid leaves the exchanger 140 through a first outlet 142 and goes towards a first heat exchange zone 125 of the cold zone 121. Once the first exchange zone 125 has been crossed, the fluid goes again towards the exchanger 140 and enters through the second inlet 143 and comes out through the second outlet 144 and goes towards a second heat exchange zone 126 of the cold zone 121. Once the second heat exchange zone 126 crossing, the fluid goes again to the exchanger 140 and enters through the third inlet 145 and leaves through the third outlet 146 and goes to the second buffer tank 153 configured to smooth the pressure of the fluid leaving the exchanger 140. The fluid then passes through the second check valve 151, which is configured in the same flow direction as the first check valve 150.
  • the heat transfer fluid passes through the heat exchanger 140 three times, the thermal conductance in operation is thus increased up to 0.35W/K, with a cooler on/off thermal conductance ratio of at least 1750.
  • the coolant can pass six times or more through the heat exchanger 140.
  • the cryogenic cooler 100 according to the invention is shown comprising a circuit 130 according to a third embodiment.
  • the third embodiment differs from the embodiments illustrated in figure 1 , 2 , 4 And 5 in that it does not include a direct line 131 between the first and the second non-return valve 150, 151.
  • the heat transfer fluid circulates throughout the cold zone 121.
  • the heat transfer fluid flows from the direct line 131 to the first non-return valve 150.
  • the fluid reaches a first buffer tank 152 configured to smooth the fluid pressure within the circuit 130.
  • the heat transfer fluid goes towards a first fluid inlet 141 of the application heat exchanger 140 configured to exchange with a first device to be cooled.
  • the fluid leaves the exchanger 140 through a first outlet 142.
  • the heat transfer fluid then goes to a first fluid inlet 341 of a second application heat exchanger 241 configured to exchange with a second device to be cooled.
  • the fluid leaves the exchanger 241 through a first outlet 342.
  • the heat transfer fluid then goes to a first fluid inlet 441 of a third application heat exchanger 242 configured to exchange with a third device to be cooled.
  • the fluid leaves the exchanger 242 through a first outlet 442.
  • the heat transfer fluid finally goes to a second buffer tank 153 configured to again smooth the pressure of the fluid leaving the exchanger.
  • the fluid then passes through the second check valve 151, which is configured in the same flow direction as the first check valve 150.
  • the heat transfer fluid flows from the direct line 131 to the first non-return valve 150.
  • the fluid reaches a first buffer tank 152 configured to smooth the fluid pressure within the circuit 130.
  • the heat transfer fluid goes towards a first fluid inlet 141 of the application heat exchanger 140 configured to exchange with a first device to be cooled.
  • the fluid leaves the exchanger 140 through a first outlet 142 and goes towards a first heat exchange zone 125 of the cold zone 121. Once the first exchange zone 125 has been crossed, the fluid then goes towards a first fluid inlet 341 of a second application heat exchanger 241 configured to exchange with a second device to be cooled.
  • the fluid leaves the exchanger 241 through a first outlet 342 and goes towards a second heat exchange zone 126 of the cold zone 121. Once the second exchange zone 126 has been crossed, the fluid then goes towards a first fluid inlet 441 of a third application heat exchanger 242 configured to exchange with a third device to be cooled. The fluid exits the exchanger 242 through a first outlet 442. The heat transfer fluid finally goes to a second buffer tank 153 configured to again smooth the pressure of the fluid exiting the exchanger. The fluid then passes through the second check valve 151, which is configured in the same flow direction as the first check valve 150.
  • the cryogenic cooler 100 differs from that previously described in that the cold finger 120 is not in fluid communication with said heat transfer fluid circuit 130 and in that it comprises a small wave generator pressure and flow 110 fluidly connected to the cold end of the circuit 130 of heat transfer fluid.
  • the cryogenic cooler 100 differs from that previously described in that the cold finger 120 is not in fluid communication with said heat transfer fluid circuit 130 and in that it comprises a direct T branch 160 fluidly connecting the pressure and flow wave generator 110 and the cold finger 120.
  • a heating switch is activated as soon as the chiller is turned on.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Photometry And Measurement Of Optical Pulse Characteristics (AREA)

Claims (16)

  1. Kryokühler (100), umfassend:
    - mindestens einen Druck- und Strömungswellengenerator (110),
    - mindestens einen Kühlfinger (120), einen Kaltbereich (121) umfassend, wobei der Druck- und Strömungswellengenerator (110) fluidisch mit dem Kühlfinger (120) verbunden ist,
    - mindestens einen Kreislauf (130) des Wärmeträgerfluids,
    - mindestens einen Anwendungswärmetauscher (140), konfiguriert, um Kalorien mit mindestens einer Kühlvorrichtung auszutauschen,
    dadurch gekennzeichnet, dass der Kühler (100) mindestens umfasst:
    - ein erstes Rückschlagventil (150) und ein zweites Rückschlagventil (151), die im Kreislauf (130) angeordnet sind, wobei mindestens ein Rückschlagventil (150, 151) vom dem ersten und dem zweiten Rückschlagventil (150, 151) ein passives Rückschlagventil ist, wobei das erste Rückschlagventil (150) und das zweite Rückschlagventil (151) fluidisch mit dem Kühlfinger (120) verbunden sind,
    - mindestens einen Anwendungswärmetauscher (140), mindestens einen ersten Fluideinlass (141) umfassend, der stromabwärts des ersten Rückschlagventils (150) in der Zirkulationsrichtung des Wärmeträgerfluids angeordnet ist, und mindestens einen ersten Fluidauslass (142), der stromaufwärts des zweiten Rückschlagventils (151) in der Zirkulationsrichtung des Wärmeträgerfluids angeordnet ist.
  2. Kryokühler nach Anspruch 1, wobei mindestens eines der zwei, vorzugsweise jedes Rückschlagventil (150, 151), eine oder mehrere Tesla-Dioden in Reihe umfasst.
  3. Kryokühler nach einem der Ansprüche 1 oder 2, wobei der Anwendungswärmetauscher (140) eine Vielzahl von Einlässen (141, 143, 145) umfasst, die einer Vielzahl von Fluidauslässen (142, 144, 146) zugeordnet sind.
  4. Kryokühler nach einem der Ansprüche 1 bis 3, wobei der Kaltbereich (121) mindestens einen ersten Wärmetauschbereich (125) umfasst, in dem das Wärmeträgerfluid zirkuliert.
  5. Kryokühler nach den Ansprüchen 3 und 4 in Kombination, wobei der erste Fluidauslass (142) des Anwendungswärmetauschers (140) fluidisch mit dem ersten Wärmetauschbereich (125) des Kaltbereichs (121) verbunden ist, wobei der erste Fluidauslass (142) stromaufwärts des ersten Wärmetauschbereichs (125) des Kaltbereichs (121) in der Zirkulationsrichtung des Wärmeträgerfluids angeordnet ist.
  6. Kryokühler nach den Ansprüchen 3 und 4 in Kombination oder nach Anspruch 5, wobei der zweite Fluideinlass (143) des Anwendungswärmetauschers (140) fluidisch mit dem ersten Wärmetauschbereich (125) des Kaltbereichs (121) verbunden ist, wobei der zweite Fluideinlass (143) stromabwärts des ersten Wärmetauschbereichs (125) des Endes (121) des Kaltbereichs (121) in der Zirkulationsrichtung des Wärmeträgerfluids angeordnet ist.
  7. Kryokühler nach einem der Ansprüche 1 bis 6, eine Vielzahl von Anwendungswärmetauschern umfassend, die jeweils mindestens einen Wärmeträgerfluideinlass (141, 143, 145) und einen Wärmeträgerfluidauslass (142, 144, 146) umfassen, einen Wärmetauschbereich bildend.
  8. Kryokühler nach einem der Ansprüche 1 bis 7, mindestens einem ersten Pufferbehälter (152) umfassend, der stromabwärts des ersten Rückschlagventils (150) in der Zirkulationsrichtung des Wärmeträgerfluids angeordnet ist, und konfiguriert ist, um die Druck- und Strömungswelle zu glätten, die auf der Höhe des Kaltbereichs (121) extrahiert wird.
  9. Kryokühler nach einem der Ansprüche 1 bis 8, mindestens einen zweiten Pufferbehälter (153) umfassend, der stromaufwärts des zweiten Rückschlagventils (151) in der Zirkulationsrichtung des Wärmeträgerfluids angeordnet ist, und konfiguriert ist, um die Druck- und Strömungswelle zu glätten, die auf der Höhe des Kaltbereichs (121) ankommt.
  10. Kühler nach einem der Ansprüche 8 oder 9, wobei mindestens einer der beiden Pufferbehälter aus einem Teil des Kreislaufs des Wärmeträgerfluids geformt wird.
  11. Kühler nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Kühler (100) ein Kühler vom Typ Pulsgasrohr oder Stirling ist.
  12. Kühler nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Kühlfinger (120) in fluidischer Verbindung mit dem Kreislauf des Wärmeträgerfluids (130) steht.
  13. Kühler nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass der Kühlfinger (120) nicht in fluidischer Verbindung mit dem Kreislauf des Wärmeträgerfluids (130) steht, und dass er einen kleinen Druck- und Strömungswellengenerator (110) aufweist, der fluidisch an das kalte Ende des Kreislaufs des Wärmeträgerfluids (130) angeschlossen ist.
  14. Kühler nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass der Kühlfinger (120) nicht in fluidischer Verbindung mit dem Kreislauf des Wärmeträgerfluids (130) steht, und dass er einen direkten T-Abzweiger (160) aufweist, der fluidisch den Druck- und Strömungswellengenerator (110) und den Kühlfinger (120) verbindet.
  15. Kühler nach einem der vorhergehenden Ansprüche, eine Vielzahl von Anwendungswärmetauschern umfassend, die konfiguriert sind, um Kalorien mit einer Vielzahl von Kühlvorrichtungen auszutauschen.
  16. Raumfahrteinheit, mindestens einem Strahlungsdetektor und einen Kryokühler (100) nach einem der vorhergehenden Ansprüche umfassend, wobei der Anwendungswärmetauscher (140) des Kühlers zum Kühlen des Strahlungsdetektors konfiguriert ist.
EP20747050.1A 2019-06-26 2020-06-26 Kryokühler für einen strahlungsdetektor, insbesondere in einem raumfahrzeug Active EP3990839B1 (de)

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FR1906948A FR3097948B1 (fr) 2019-06-26 2019-06-26 Refroidisseur cryogénique pour détecteur de rayonnement notamment dans un engin spatial
PCT/FR2020/051123 WO2020260842A1 (fr) 2019-06-26 2020-06-26 Refroidisseur cryogénique pour détecteur de rayonnement notamment dans un engin spatial

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EP3990839B1 true EP3990839B1 (de) 2023-07-12

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US1329559A (en) 1916-02-21 1920-02-03 Tesla Nikola Valvular conduit
US6637211B1 (en) 2002-08-13 2003-10-28 The Regents Of The University Of California Circulating heat exchangers for oscillating wave engines and refrigerators
CN100557345C (zh) 2006-05-16 2009-11-04 中国科学院理化技术研究所 一种压力波驱动的非共振型直流换热器
EP2562489B1 (de) * 2010-04-23 2020-03-04 Sumitomo Heavy Industries, LTD. Kühlsystem und -verfahren
JP2012255734A (ja) 2011-06-10 2012-12-27 Shimadzu Corp スターリング冷凍機冷却式検出器
CN105745553B (zh) * 2013-11-13 2019-11-05 皇家飞利浦有限公司 包括热学有效的跨越系统的超导磁体系统以及用于冷却超导磁体系统的方法
WO2018065458A1 (en) * 2016-10-06 2018-04-12 Koninklijke Philips N.V. Passive flow direction biasing of cryogenic thermosiphon

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FR3097948B1 (fr) 2021-06-25
FR3097948A1 (fr) 2021-01-01
EP3990839A1 (de) 2022-05-04
US11976873B2 (en) 2024-05-07
JP2022538133A (ja) 2022-08-31
WO2020260842A1 (fr) 2020-12-30
US20220412637A1 (en) 2022-12-29

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