EP0614059A1 - Kühler mit einem Schwingrohrkaltkopf - Google Patents

Kühler mit einem Schwingrohrkaltkopf Download PDF

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Publication number
EP0614059A1
EP0614059A1 EP94400432A EP94400432A EP0614059A1 EP 0614059 A1 EP0614059 A1 EP 0614059A1 EP 94400432 A EP94400432 A EP 94400432A EP 94400432 A EP94400432 A EP 94400432A EP 0614059 A1 EP0614059 A1 EP 0614059A1
Authority
EP
European Patent Office
Prior art keywords
tube
regenerator
cold finger
pressure
oscillator
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.)
Granted
Application number
EP94400432A
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English (en)
French (fr)
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EP0614059B1 (de
Inventor
Damien Feger
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Cryotechnologies SA
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Cryotechnologies SA
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Filing date
Publication date
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Publication of EP0614059A1 publication Critical patent/EP0614059A1/de
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Publication of EP0614059B1 publication Critical patent/EP0614059B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F25B9/14—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1406—Pulse-tube cycles with pulse tube in co-axial or concentric geometrical arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1408—Pulse-tube cycles with pulse tube having U-turn or L-turn type geometrical arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1417—Pulse-tube cycles without any valves in gas supply and return lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1424—Pulse tubes with basic schematic including an orifice and a reservoir
    • F25B2309/14241—Pulse tubes with basic schematic including an orifice reservoir multiple inlet pulse tube

Definitions

  • the present invention relates to coolers based on the Stirling cycle. These coolers allow cryogenic temperatures to be reached.
  • coolers include an electromechanical oscillator which generates, in an active enclosure containing a fluid, a pressure wave.
  • the enclosure comprises a part provided with a mobile regenerator or displacer which uses the expansion and compression cycles of the fluid to carry out a Stirling cycle.
  • the fluid used is generally helium, at an average pressure of several hundred kilopascals.
  • the oscillator can be rotary or linear.
  • the cold part generally has, in order to limit the heat losses by conduction and to facilitate its manufacture, the shape of a very elongated cylinder which earns it the name of "cold finger".
  • the free end of the cold finger provides cooling power created by the expansion of the fluid.
  • the base of the cold finger connected to the oscillator, dissipates the heat created by the compression of the fluid.
  • the cold finger is generally immersed in a cryostat, such as a Dewar vessel for example, which contains the device to be cooled.
  • the interior of the cryostat is generally subjected to vacuum to limit the entry of heat.
  • the oscillator and the cold finger are one piece.
  • the movement of regenerator is generally provided, in the case of a rotary oscillator, by the oscillator piston. This configuration is very compact, it limits the pressure drops between the oscillator and the cold finger. However, the vibrations induced by the oscillator are transmitted to the device to be cooled.
  • the oscillator and the cold finger are separated but connected by a pneumatic conduit which ensures the transfer of the pressure wave between the oscillator and the cold finger.
  • the movement of the regenerator can be ensured by a specific motor or by the pneumatic effects generated by the pressure wave.
  • the first configuration is generally used in space applications. These two configurations make it possible to separate the oscillator and the equipment to be cooled, which facilitates the integration of the cooler into the environment of the device to be cooled. In addition, these two configurations make it possible to considerably reduce the vibrations at the level of the device to be cooled.
  • Mobile regenerator coolers have a relatively high cost because of the machining tolerances required to produce the regenerator and the cold finger which are in movement with respect to each other.
  • Pulsed tube type cold finger coolers are also known.
  • the cold finger instead of containing a mobile regenerator contains a fixed regenerator and a pulsed tube.
  • coolers are numerous.
  • the lifespan of the cold finger is almost unlimited because the elimination of movement reduces wear.
  • the vibrations induced in the cold finger are much lower than those induced in the cold fingers with mobile regenerator.
  • the costs are also much lower due to an operation less sensitive to geometric manufacturing tolerances.
  • Fixed regenerator reduces losses efficiency linked to the shuttle effect and fluid leaks between the outer wall of the cold finger and the regenerator.
  • These coolers insofar as they use a pulsed tube with double orifice, have an efficiency substantially equivalent to that of a cold finger cooler provided with a mobile regenerator.
  • a double orifice pulsed tube cooler is described later in Figure 1.
  • the major drawback of this type of cooler is linked to the U shape of the cold finger.
  • One of the branches of the U is produced by the regenerator and the other by the pulsed tube.
  • the base of the U which is also the free end of the cold finger is formed of an end piece integral with one side of the regenerator and the other of the pulsed tube.
  • This cold finger imposes a specific cryostat and therefore prevents its implantation in a cryostat intended for a cold finger with mobile regenerator or of the Joule-Thomson type. Maintenance "on the ground” of the cold finger with pulsed tube is not possible while intervention on a cold finger with mobile regenerator is easy. Indeed, it would be necessary to break the vacuum of the cryostat to dismantle the pulsed tube or the regenerator.
  • the present invention aims to remedy these drawbacks. It offers a cooler based on the Stirling cycle, fitted with a cold finger of the pulsed tube type. This cooler can be installed in a conventional cryostat and it has good thermodynamic performance.
  • the cooler according to the invention comprises means for generating a pressure wave in a fluid and transmitting it to a cold finger of the pulsed tube type.
  • the cold finger comprises a regenerator pneumatically connected to the pulsed tube, this regenerator is tubular and is mounted coaxially around the pulsed tube.
  • the regenerator can, for example, be contained between an outer tube and an inner tube, the inner tube serving as a pulsed tube.
  • the regenerator can be contained in an outer tube, the inner surface of the regenerator serving as a pulsed tube.
  • the external tube serves as an interior wall for the cryostat. This configuration, which removes the inner wall of the cryostat, improves cooling performance by reducing losses by conduction.
  • FIG. 1 represents a cooler based on the Stirling cycle provided with a cold finger 1 of the pulsed tube type 5, according to known art.
  • the cold finger 1 is connected to a pressure oscillator 2 through a base 3.
  • the base 3 provides the mechanical interface and the seal between the cold finger 1 and a cryostat in which the cold finger 1 is generally immersed.
  • 'base 3 forms the base of the cold finger 1.
  • the cryostat is not shown for reasons of clarity.
  • the pressure oscillator 2 generates a pressure wave in a fluid and the fluid is successively compressed and expanded.
  • the cold finger 1 comprises a fixed regenerator 4 contained in a tube 7 and a pulsed tube 5 which form the two branches of a U.
  • the regenerator 4 has the shape of a full cylinder.
  • the base of the U is produced by a cold end piece 6 which pneumatically connects the regenerator 4 and the pulsed tube 5.
  • the tube 7 containing the regenerator has a hot end fixed to the base 3 and a cold end fixed to the end piece 6.
  • the end piece 6 constitutes the free end of the cold finger 1. This is the point the cooler the cooler. It also serves to transmit to the device to be cooled, placed nearby, the frigories made available by the expansion of the fluid.
  • the fixed regenerator 4 operates in the same way as a mobile regenerator. It is made of a porous material permeable to fluid.
  • the regenerator 4 is pneumatically connected to the oscillator 2.
  • regenerator The function of the regenerator is to capture cold from the fluid when the latter is sucked in by the oscillator 2 during the expansion phase and to evacuate heat to this fluid when it is discharged during the compression phase.
  • the pulsed tube 5 simply consists of a tube substantially parallel to the tube 7 containing the regenerator 4. It is integral with one cold end of the end piece 6 and the other hot end of the base 3.
  • a pneumatic circuit 8 is used to connect the pressure oscillator 2 to the regenerator 4 and to the pulsed tube 5.
  • a buffer tank 9 is also provided and connected to the pneumatic circuit 8. It has a sufficient volume so that the fluid which it contains remains at a substantially constant pressure whatever the phase of the pressure oscillator 2. When the oscillator sucks in the fluid, the fluid in the buffer tank 9 feeds the pulsed tube 5 and when the oscillator 2 discharges, the discharged fluid fills the buffer tank 9.
  • the pneumatic circuit comprises a first conduit 8 connecting the regenerator 4 to the oscillator 2, a second conduit 82 connecting the hot end of the pulsed tube 5 to the buffer tank 9 and a third conduit 83 connecting the hot end of the pulsed tube to the pressure oscillator 2.
  • the pulsed tube is connected both to the oscillator and to the buffer tank.
  • the fluid passes through a hot heat exchanger 10 between the hot end of the pulsed tube 5 and the oscillator 2 and / or the buffer tank 9.
  • This hot exchanger 10 can be housed in the base 3.
  • the third conduit 83 is disposed between the first conduit 81 and the second conduit 82 and it reaches the second conduit 82 between the buffer tank 9 and the hot heat exchanger 10.
  • the hot heat exchanger 10 collects the heat of compression of the fluid leaving the pulsed tube and its evacuation, via the base 3, to the outside of the cooler.
  • the movement of the fluid in the cold finger is out of phase with respect to the pressure wave generated by the oscillator 2.
  • the phase shift and the flow rates at the hot ends of the pulsed tube 5 and of the tube 7 containing the regenerator 4 are a function of the pneumatic impedance of the conduits 81, 82 and 83 and of the volume of the buffer tank 9.
  • the pneumatic impedance of the conduits can be adjusted by an appropriate choice of their section, their length.
  • the conduits can also include simple pinches or orifices 11 calibrated as in FIG. 1 or even valves.
  • the behavior of the fluid in the pulsed tube is as follows: let us consider a volume A of fluid which transits between the cold end of the pulsed tube 5 and the end piece 6. Due to the phase shift of the movement of the fluid in the cold finger with the expansion and compression phases of the oscillator 2, this fluid when it relaxes passes to the end piece 6 while cooling it and when it compresses, enters the pulsed tube 5 where it heats up almost adiabatic way.
  • FIG. 2 schematically represents a cooler according to the invention.
  • This cooler is comparable to that of FIG. 1.
  • the main difference is at the level of the cold finger 21 which, instead of comprising a regenerator and a pulsed tube configured in U, comprises a tubular regenerator 24 mounted coaxially around the pulsed tube 25.
  • the cold finger 21 is always connected to an oscillator 2 through a base 3.
  • the base 3 plays the same role as in FIG. 1.
  • the free end of the cold finger always ends with an end piece 26. It is always the coldest part of the cooler.
  • the regenerator 24 plays the same role as in the known art. Instead of having the shape of a full cylinder it now has the shape of a tube.
  • the regenerator 24 is contained between an outer tube 27 and an inner tube 28.
  • the cylindrical outer tube 27 has a hot end tightly fixed to the base 3 and a cold end tightly fixed to the end piece 26. It forms the outer surface of the cold finger 21.
  • This outer tube 27 preferably has a thickness as thin as possible to limit thermal entry along the cold finger. It is preferably carried out in a material with as low a thermal conductivity as possible, for example stainless steel.
  • This external tube 27 as well as its attachments to the base 3 and to the end piece 26 must seal the interior of the cold finger vis-à-vis the external environment.
  • the cold finger is generally immersed in a cryostat subjected to vacuum. This cryostat is represented with the reference 30 in FIG. 4 in the form of a Dewar vase.
  • the inner tube 28 serves both as a pulsed tube and as an inner wall to the tubular regenerator 24. It is arranged coaxially in the external tube 27 and has a hot end fixed to the base 3. Its other end which is cold opens into the end piece 26.
  • This internal tube 28 is not subjected like the external tube 27 to significant pressure differences. It does not have to be tightly sealed like the outer tube. It avoids direct passage of the fluid from the regenerator 24 to the pulsed tube 25 without passing through the end piece 26.
  • the design of this internal tube 28 with respect to the choice of the constituent material, its method of fixing, and its thickness can be more easily optimized. One can even consider physically removing the inner tube 28 if the inner surface of the regenerator 24 is sealed. In this case, it is the interior surface of the regenerator which serves as a pulsed tube.
  • the end piece 26 resembles the end pieces of the cold fingers with mobile regenerator.
  • the regenerator and the pulsed tube communicate pneumatically thanks to it.
  • the thickness of the end piece 26 will be as small as possible. It will be made of a material having as high a thermal conductivity as possible: copper for example. It is conceivable that the end piece contains a cold exchanger 29 formed for example of copper grids brazed at their periphery. This cold exchanger 29 improves the heat exchange between the fluid and the end piece 26.
  • the material of the end piece 26 will preferably have a coefficient of expansion as low as possible when the cold finger 21 is used to cool a device placed directly on the end piece 26 (technique known by the English name Integrated Dewar Cooler Assembly).
  • the end piece 26 may, for example, be provided with a tranquilizer device to ensure the lowest possible level of turbulence in the pulsed tube 25. It is indeed desirable to maintain a large thermal gradient between the two hot ends and cold from the pulsed tube.
  • This transquilliser device can be produced by a honeycomb part or by the cold exchanger 29.
  • the other elements of the cooler, namely the oscillator 2, the pneumatic circuit 8, the buffer tank 9 and the hot exchanger 10 are comparable to those in Figure 1.
  • the hot heat exchanger 10 if it is configured with grids or a honeycomb material also has a role of tranquilizer.
  • the optimal adjustment of the phase shift and the amplitude of the fluid flow rates in the regenerator 24 and the pulsed tube 25 will depend on the volume of the buffer tank 9 and on the characteristics of the conduits 81, 82, 83 as before.
  • the pulsed tube has a length of 70 mm and that in operation its extreme temperatures are 80 ° K at the cold end and 300 ° K at the hot end. It is assumed that the thermal gradient is linear in the wall of the pulsed tube, that the average pressure in the pulsed tube is 35.105Pa and that it varies more or less 106Pa, because of the pressure wave.
  • the slice of fluid will have an average temperature of 190 ° K but during the expansion and compression cycles, it will see its temperature oscillate between 166 ° K and 210 ° K (curve C1). This slice of fluid will be vis-à-vis with a section of pulsed tube whose temperatures will be between 158 ° K and 221 ° K (curve C2) because of the linear thermal gradient.
  • the fluid In the expansion phase, the fluid will be in contact with a portion of the pulsed tube cooler than it and will tend to give it heat.
  • the fluid Symmetrically, in the compression phase, the fluid will be in contact with a portion of the pulsed tube hotter than it and will tend to extract heat from it. This heat pumping effect from the hot end of the pulsed tube to the cold end is detrimental to the performance of the cooler.
  • These heat exchanges with the walls concern only part of the fluid: the thermal boundary layer which is close enough to the wall to have time to exchange, mainly by gas conduction, heat during a compression-expansion cycle.
  • a cooler according to the invention makes it possible to reduce the exchanges between the fluid and the wall of the pulsed tube by placing the pulsed tube inside the regenerator and not around it.
  • the cold finger is formed of two coaxial tubes (of zero thickness for simplicity) of diameters 5mm and 3.5mm, in the case of a thickness of thermal boundary layer of 0.2 mm, it can be estimated that only 20% of fluid participates in the heat exchange with the wall of the pulsed tube, if the pulsed tube is placed inside the regenerator, while more than 50% of fluid participates in the heat exchange with the external and internal walls of the tube pulsed, if the regenerator is placed inside the pulsed tube.
  • FIGS. 4 to 7 show various variants of a cooler according to the invention. We refer to figure 4.
  • the cold finger is immersed in a cryostat such as a Dewar vessel 30 comprising two chambers 31, 32 inserted one inside the other and separated by a vacuum.
  • the internal enclosure 32 has the shape of a well.
  • the cooling device referenced 33 is disposed between the external enclosure 31 and the internal enclosure 32. It is fixed to the bottom of the well.
  • a thermal coupler 34 is inserted between the free end of the cold finger 21 and the bottom of the well to optimize the cooling of the device to be cooled 33.
  • the pressure oscillator 2 is rotary.
  • the buffer tank is constituted by the casing 35 of the oscillator, which saves space.
  • the second conduit 82 and the third conduit 83 each comprise a valve 36 instead of a calibrated orifice and, moreover, the second conduit 82 is provided with a pinch 37 between the valve and the hot exchanger 10.
  • the cold finger and the base are represented by a single block 50 for simplicity.
  • the pressure oscillator 51 is a resonant linear oscillator.
  • the buffer tank 52 is provided with a heating device 54.
  • the temperature of the fluid in the buffer tank 52 is adjustable so as to be able to adjust the average pressure in the cooler and to be able to adjust the resonant frequency of the cooler. this is particularly advantageous in the case where the cooler is used in a satellite where an adjustable frequency is sought in order to avoid exciting the platform or instruments near the cooler.
  • the hot exchanger is constituted by a fin device 55 or equivalent.
  • This device 55 is arranged on the second conduit 82 connecting the pulsed tube to the buffer tank 52.
  • the other conduits 81, 83 and the reservoir 52 could also participate in the evacuation of the heat of compression of the fluid. To this end, they would be fitted with devices, with fins for example, improving the dissipation of this heat to the outside.
  • the buffer tank 52 is provided with a tranquilizer device 56 to ensure a level of turbulence as low as possible in the pulsed tube.
  • This tranquilizer device 56 can be of the same nature as that described in the end piece 26 of FIG. 2.
  • the cold finger 60 immersed in a cryostat 61, and the rotary pressure oscillator 68 form a monobloc cooler.
  • the compressor casing 69 constitutes the buffer tank.
  • the cold finger 60 comprises an external tube 62, a tubular regenerator 63 and a pulsed tube 66.
  • the external tube 62 serves as an interior wall for the cryostat.
  • the inner surface of the tubular regenerator serves as a pulsed tube 66.
  • the removal of the inner wall of the cryostat can of course be used in other configurations.
  • the cooling device 65 is directly fixed to the end piece 64 which connects the pulsed tube and the regenerator. Cooling is improved compared to the configuration where the outer tube and the inner wall of the cryostat are separate.
  • a cooling device 67 with fluid circulation has been placed around the hot exchanger 10. This cooling device is preferably used when the pulsed tube is subjected to significant powers, for example greater than a few watts.
  • a fluid circulation cooling device one could have used a cooling device with natural or forced convection with air for example.
  • the configuration shown is particularly compact, it minimizes the pressure drops between the oscillator 68 and the cold finger 60.
  • the cooler now comprises several pressure oscillators 70, 71, 72 mounted in parallel.
  • a switch 73 having several input channels and an output channel makes it possible to connect the cold finger to one of the pressure oscillators 71.
  • the pressure oscillator With a cold finger without moving part, the only element presenting a relatively high risk of failure is the pressure oscillator which has moving parts.
  • the switching from one pressure oscillator to another can be controlled by the user or automatically when the operation of the oscillator in service is no longer normal. This switching does not require any intervention or disassembly on the cold finger and the cryostat, it can be carried out instantly and remotely.
  • the cooler according to the invention can cool any device, in particular sensors or detectors, electronic components, samples, etc.
EP19940400432 1993-03-02 1994-03-01 Kühler mit einem Schwingrohrkaltkopf Expired - Lifetime EP0614059B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9302376A FR2702269B1 (fr) 1993-03-02 1993-03-02 Refroidisseur muni d'un doigt froid du type tube pulsé.
FR9302376 1993-03-02

Publications (2)

Publication Number Publication Date
EP0614059A1 true EP0614059A1 (de) 1994-09-07
EP0614059B1 EP0614059B1 (de) 1998-12-16

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EP19940400432 Expired - Lifetime EP0614059B1 (de) 1993-03-02 1994-03-01 Kühler mit einem Schwingrohrkaltkopf

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EP (1) EP0614059B1 (de)
DE (1) DE69415187T2 (de)
FR (1) FR2702269B1 (de)

Cited By (20)

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EP0717245A2 (de) * 1994-12-12 1996-06-19 Hughes Aircraft Company Konzentrischer Stossrohrentspanner
FR2736710A1 (fr) * 1995-07-12 1997-01-17 Commissariat Energie Atomique Refrigerateur ou pompe a chaleur a tube de pulsation alimente par un generateur de pression
FR2743871A1 (fr) * 1996-01-24 1997-07-25 Hughes Aircraft Co Detendeur pour refroidisseur concentrique a tube a pulsion, ce refroidisseur et systeme de refroidissement l'utilisant
EP0803687A1 (de) * 1996-04-23 1997-10-29 Cryotechnologies Kryostat für Tiefsttemperatur-Kälteanlage und Kälteanlagen mit einem solchen Kryostat
FR2760076A1 (fr) * 1997-02-21 1998-08-28 Cryotechnologies Dispositif de refroidissement cryogenique a oscillateur de pression a double effet
WO1999020957A1 (en) * 1997-10-20 1999-04-29 Cornelis Maria De Blok Thermo-acoustic system
US5968637A (en) * 1996-05-07 1999-10-19 Thomson-Csf Use of nitride barrier to prevent the diffusion of silver in glass
EP1158256A3 (de) * 2000-05-25 2002-01-02 Cryomech, Inc. Schwingrohrtieftemperaturkältegerät mit einem integrierten Dämpfvolumen
WO2002004875A1 (en) * 2000-07-05 2002-01-17 Raytheon Company Apparatus and method for achieving temperature stability in a two-stage cryocooler
FR2821150A1 (fr) * 2001-02-17 2002-08-23 Lg Electronics Inc Refregirateur a tube pulse
US6725670B2 (en) 2002-04-10 2004-04-27 The Penn State Research Foundation Thermoacoustic device
US6755027B2 (en) 2002-04-10 2004-06-29 The Penn State Research Foundation Cylindrical spring with integral dynamic gas seal
US6792764B2 (en) 2002-04-10 2004-09-21 The Penn State Research Foundation Compliant enclosure for thermoacoustic device
WO2006078437A1 (en) * 2005-01-19 2006-07-27 Raytheon Company Multi-stage cryocooler with concentric second stage
EP1952076A2 (de) * 2005-10-31 2008-08-06 Clever Fellows Innovation Consortium, Inc. Akustische kühlvorrichtung mit getrenntem kühlkopf und resonantem treiber
CN100424443C (zh) * 2007-06-04 2008-10-08 中国科学院上海技术物理研究所 一种用于同轴型脉管制冷机的整体式冷头
WO2009075911A1 (en) * 2007-12-12 2009-06-18 Carleton Life Support Systems Inc. Field integrated pulse tube cryocooler with sada ii compatibility
CN101298947B (zh) * 2008-06-26 2010-06-09 上海交通大学 螺纹焊接整体狭缝式同轴脉管制冷机
CN103884126A (zh) * 2012-12-19 2014-06-25 中国科学院理化技术研究所 同轴型脉冲管制冷机
CN109140813A (zh) * 2016-11-16 2019-01-04 浙江大学 压缩机与制冷机冷头耦合用l型声学匹配组件及制冷机

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GB1202203A (en) * 1966-08-02 1970-08-12 Hymatic Eng Co Ltd Improvements relating to refrigerating apparatus
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US2824430A (en) * 1954-02-18 1958-02-25 Philips Corp Cold-gas refrigerator control system
US3188818A (en) * 1963-11-12 1965-06-15 Little Inc A Refrigeration method and apparatus embodying fluid expansion
GB1202203A (en) * 1966-08-02 1970-08-12 Hymatic Eng Co Ltd Improvements relating to refrigerating apparatus
US3877239A (en) * 1974-03-18 1975-04-15 Hughes Aircraft Co Free piston cryogenic refrigerator with phase angle control
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EP0717245A2 (de) * 1994-12-12 1996-06-19 Hughes Aircraft Company Konzentrischer Stossrohrentspanner
EP0717245A3 (de) * 1994-12-12 1996-07-10 Hughes Aircraft Co
US5613365A (en) * 1994-12-12 1997-03-25 Hughes Electronics Concentric pulse tube expander
FR2736710A1 (fr) * 1995-07-12 1997-01-17 Commissariat Energie Atomique Refrigerateur ou pompe a chaleur a tube de pulsation alimente par un generateur de pression
WO1997003327A1 (fr) * 1995-07-12 1997-01-30 Commissariat A L'energie Atomique Refrigerateur ou pompe a chaleur a tube de pulsation alimente par un generateur de pression
FR2743871A1 (fr) * 1996-01-24 1997-07-25 Hughes Aircraft Co Detendeur pour refroidisseur concentrique a tube a pulsion, ce refroidisseur et systeme de refroidissement l'utilisant
EP0803687A1 (de) * 1996-04-23 1997-10-29 Cryotechnologies Kryostat für Tiefsttemperatur-Kälteanlage und Kälteanlagen mit einem solchen Kryostat
US5968637A (en) * 1996-05-07 1999-10-19 Thomson-Csf Use of nitride barrier to prevent the diffusion of silver in glass
FR2760076A1 (fr) * 1997-02-21 1998-08-28 Cryotechnologies Dispositif de refroidissement cryogenique a oscillateur de pression a double effet
WO1999020957A1 (en) * 1997-10-20 1999-04-29 Cornelis Maria De Blok Thermo-acoustic system
US6314740B1 (en) 1997-10-20 2001-11-13 Cornelis Maria De Blok Thermo-acoustic system
EP1158256A3 (de) * 2000-05-25 2002-01-02 Cryomech, Inc. Schwingrohrtieftemperaturkältegerät mit einem integrierten Dämpfvolumen
US6378312B1 (en) 2000-05-25 2002-04-30 Cryomech Inc. Pulse-tube cryorefrigeration apparatus using an integrated buffer volume
WO2002004875A1 (en) * 2000-07-05 2002-01-17 Raytheon Company Apparatus and method for achieving temperature stability in a two-stage cryocooler
FR2821150A1 (fr) * 2001-02-17 2002-08-23 Lg Electronics Inc Refregirateur a tube pulse
US6755027B2 (en) 2002-04-10 2004-06-29 The Penn State Research Foundation Cylindrical spring with integral dynamic gas seal
US6792764B2 (en) 2002-04-10 2004-09-21 The Penn State Research Foundation Compliant enclosure for thermoacoustic device
US7055332B2 (en) 2002-04-10 2006-06-06 The Penn State Research Foundation Compliant enclosure for thermoacoustic device
US7143586B2 (en) 2002-04-10 2006-12-05 The Penn State Research Foundation Thermoacoustic device
US6725670B2 (en) 2002-04-10 2004-04-27 The Penn State Research Foundation Thermoacoustic device
WO2006078437A1 (en) * 2005-01-19 2006-07-27 Raytheon Company Multi-stage cryocooler with concentric second stage
US7296418B2 (en) 2005-01-19 2007-11-20 Raytheon Company Multi-stage cryocooler with concentric second stage
EP1952076A4 (de) * 2005-10-31 2010-10-13 Clever Fellows Innovation Cons Akustische kühlvorrichtung mit getrenntem kühlkopf und resonantem treiber
EP1952076A2 (de) * 2005-10-31 2008-08-06 Clever Fellows Innovation Consortium, Inc. Akustische kühlvorrichtung mit getrenntem kühlkopf und resonantem treiber
CN100424443C (zh) * 2007-06-04 2008-10-08 中国科学院上海技术物理研究所 一种用于同轴型脉管制冷机的整体式冷头
WO2009075911A1 (en) * 2007-12-12 2009-06-18 Carleton Life Support Systems Inc. Field integrated pulse tube cryocooler with sada ii compatibility
US8079224B2 (en) 2007-12-12 2011-12-20 Carleton Life Support Systems, Inc. Field integrated pulse tube cryocooler with SADA II compatibility
CN101298947B (zh) * 2008-06-26 2010-06-09 上海交通大学 螺纹焊接整体狭缝式同轴脉管制冷机
CN103884126A (zh) * 2012-12-19 2014-06-25 中国科学院理化技术研究所 同轴型脉冲管制冷机
CN103884126B (zh) * 2012-12-19 2016-02-10 中国科学院理化技术研究所 同轴型脉冲管制冷机
CN109140813A (zh) * 2016-11-16 2019-01-04 浙江大学 压缩机与制冷机冷头耦合用l型声学匹配组件及制冷机
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FR2702269A1 (fr) 1994-09-09
DE69415187D1 (de) 1999-01-28
DE69415187T2 (de) 1999-05-20
EP0614059B1 (de) 1998-12-16

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