EP0803687A1 - Kryostat für Tiefsttemperatur-Kälteanlage und Kälteanlagen mit einem solchen Kryostat - Google Patents

Kryostat für Tiefsttemperatur-Kälteanlage und Kälteanlagen mit einem solchen Kryostat Download PDF

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Publication number
EP0803687A1
EP0803687A1 EP97400898A EP97400898A EP0803687A1 EP 0803687 A1 EP0803687 A1 EP 0803687A1 EP 97400898 A EP97400898 A EP 97400898A EP 97400898 A EP97400898 A EP 97400898A EP 0803687 A1 EP0803687 A1 EP 0803687A1
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EP
European Patent Office
Prior art keywords
cryostat
gas
cooler
regenerator
piston
Prior art date
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Granted
Application number
EP97400898A
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English (en)
French (fr)
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EP0803687B1 (de
Inventor
Patrick Curlier
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Thales Cryogenie SA
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Cryotechnologies SA
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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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/003—Gas cycle refrigeration machines characterised by construction or composition of the regenerator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—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 
    • F25B2309/1407—Pulse-tube cycles with pulse tube having in-line 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 
    • F25B2309/1421—Pulse-tube cycles characterised by details not otherwise provided for
    • 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 the design and production of cryogenic coolers which use a working gas following a thermodynamic cycle in a closed circuit between a compression chamber and an expansion chamber, passing through a so-called regenerative thermal accumulator, which provides a recovery exchange between compressed hot gas and expanded cold gas.
  • coolers conventionally comprise a pressure oscillator controlled to vary the volume of the compression chamber, and a cold finger terminating in the expansion chamber, in thermal contact with an element to be cooled, placed at the bottom of a thermal insulation envelope.
  • the element to be cooled is commonly an electronic component which must be kept in operation at temperatures between 60 ° K and 200 ° K, in particular in order to improve the signal to noise ratio.
  • cryogenic coolers of the type in question meet with increasing success every day, mainly when they are designed to be manufactured at low cost under shapes integrating the pressure oscillator with the cold finger in the same mechanical assembly, no longer needing external pipes to close the working gas circuit.
  • the present invention is mainly intended to provide users with a cryostat which is not limited to an envelope insulator capable of receiving the cold finger of the cooler, but which incorporates part of its essential organs, in a form allowing their interchangeable adaptation to different configurations.
  • a cryostat for cryogenic cooler produced according to the invention easily adapts, in accordance with its interchangeable nature, both to a configuration with pulsed gas tube and to a Stirling cycle configuration, and that the control of the pressure oscillator goes through a rotary crankshaft or linear type drive, depending on the expressions used by those skilled in the art, as they are included in particular in the article already cited.
  • the invention also makes it possible to bring appreciable improvements to the construction of the coolers incorporating such a cryostat and to their control mode.
  • the resulting advantages relate in particular to the combination of the cryostat with a pressure oscillator in an embodiment relating to a configuration with a pulsed gas tube.
  • the features proposed for the various components of the cryostats according to the invention have the advantage of lending themselves particularly well to the respective operating modes of the two types of coolers and of improving their own performance.
  • This is the case in particular of the provisions recommended for the regenerator, which is responsible for absorbing and releasing heat, alternately, relative to the gas which passes through it.
  • This is also the case for an exchanger advantageously provided in a cold zone, at the level of the expansion chamber, to promote heat transfer to the component to be cooled, as well as for an exchanger located in a hot zone and under pressure which is specially useful in pulsed gas type coolers, to promote heat loss to the outside.
  • the invention more specifically relates to a cryostat for a cryogenic cooler implementing a closed working gas circuit between a compression chamber located in an associated pressure oscillator casing and an expansion chamber located at the bottom of the cryostat.
  • a thermal regenerator interposed on the working gas circuit.
  • This regenerator is in annular arrangement around an axial volume extending between a cold exchanger which is in thermal contact with the component to be cooled and makes the regenerator communicate with said axial volume at the bottom of the cryostat.
  • the cryostat also includes a gas distribution ring in said regenerator, at the head of the cryostat, from a conduit drilled through the base for connection to the compression chamber.
  • the distribution ring is formed by a central piece which is mounted through said base axially at its center. Said central part is removably mounted in said base, in particular by tight screwing.
  • At least one channel for the passage of gas under controlled flow between a gas buffer tank formed inside the casing of the pressure oscillator, and the internal axial volume of the cryostat which operates in a gas tube. It is also advantageous to add one or more other channels with controlled flow allowing a withdrawal of hot gas directly at the compression outlet, at the level of the distribution ring towards the regenerator.
  • the internal volume is at on the contrary occupied by the displacement piston, which is preferably full, made of a material of low thermal conductivity, and which leaves free to the gas only the volume of the expansion chamber at the bottom of the cryostat.
  • the central part is made integral with a central tube limiting said axial volume.
  • This tube is then advantageously of the same internal diameter as the axial bore of the model intended for a connection of the cryostat to a Stirling cycle cooler. It can therefore constitute either the tube containing the pulsed gas in the first model, or the guide tube of the displacer piston of the cooler in the second case.
  • a hot exchanger positioned in the internal volume at the head of the cryostat. Its role is in the evacuation of calories which takes place by heat loss to the outside through the base and the casing of the compressor part of the cooler, made for this purpose from thermally conductive material. It is especially useful in the variant of a pulsed gas tube cooler, taking into account the heat to be evacuated at the outlet of the gas tube, which is added to the heat stored by the gas in return from the regenerator.
  • the invention provides, according to a secondary characteristic, which can be applied advantageously with the others in any operating combination, to use a structure with geometry of revolution, alternating around the axis of the cryostat, in a daisy arrangement, massive zones made of a material which is a good thermal conductor and empty zones open to the passage of gas. As a result, these areas are located in particular on horseback, on both sides, relative to a centering shoulder of the end of the central tube.
  • a cooler according to the invention constructed to operate on the principle of the pulsed gas tube, it is advantageous to provide the buffer volume of gas supplying the gas piston inside a compression piston, which at this indeed, on the side opposite to the compression chamber, is directly open in a jacket for guiding said piston which is connected to the appropriate central part of the cryostat.
  • control means comprising a crankshaft actuating a movement transmission mechanism by movable ball bearing in a groove formed transversely outside said piston.
  • the annular arrangement of the regenerator lends itself particularly well to manufacture from a sheet wound on itself.
  • the invention makes it possible to significantly improve the efficiency of the desired heat exchanges, compared with the stacks of grids or conventional balls, by using for this a sheet of suitable material, which has been previously machined, in particular by photolithographic process, so as to form separate longitudinal bands with smooth surface and transverse bars in excess thickness punctually joining the successive bands.
  • the different bands follow one another along the length of the regenerator. They form annular layers of smooth surface intersected by the intervals between bands and the bars inserted between the layers help to distribute the flow in all directions at each level of cross section.
  • the cryostat of FIG. 1 is used in combination with a pressure oscillator either to constitute a cryogenic cooler of the pulsed gas type in accordance with FIG. 6, or alternatively to constitute a cooler of the Stirling cycle type in accordance with FIG. 5.
  • a pressure oscillator either to constitute a cryogenic cooler of the pulsed gas type in accordance with FIG. 6, or alternatively to constitute a cooler of the Stirling cycle type in accordance with FIG. 5.
  • the cooler thus formed is of compact construction, the cryostat and the pressure oscillator being integrated in the same mechanical assembly.
  • cryostat according to the invention is not limited, as in the known embodiments, to a thermal insulation envelope intended to receive a cold finger previously formed in all its functional organs necessary for the implementation of the thermodynamic cycle of the working gas.
  • the passive functional members which are not subjected to displacements during operation, are provided permanently in the cryostat, the latter being constructed so as to be able to be connected, alternatively at the option of the user, to the casing a pressure oscillator belonging either to a specific cooler for implementing a Stirling cycle, or to a cooler of the pulsed gas tube type.
  • a thermal insulation envelope 1 mounted integral with a base 4 serving for its mechanical and pneumatic connection with the pressure oscillator part of the cooler.
  • concentric tubulars namely a central tube 3 and an internal wall 2 of the casing 1, which delimit between them an annular space occupied by a thermal regenerator 5.
  • the regenerator 5 is thus constructed in annular arrangement around an axial volume 6 , limited on its periphery by the central tube 3 among the two previous ferrules.
  • the other ferrule which externally limits the thermal regenerator, is therefore here directly constituted by the internal wall 2 of the thermal insulation envelope 1.
  • This is in fact, in itself conventional, of the type to double sided. Between its two walls, it is either filled with an inert gas with a low condensation point, or subjected to a high vacuum, for which it is provided with a charging port 25.
  • regenerator 5 with its own envelopes, including an external envelope which is then distinct from the internal wall 2 of the thermal insulation envelope and / or an internal envelope which is then added against the central tube 3.
  • this exchanger 8 which in operation constitutes the cold exchanger of the cooler.
  • this exchanger is designed and arranged so as to promote the transfer of the cooling power resulting from the expansion of the working gas to a component to be cooled 21, while ensuring pneumatic communication allowing the passage of the working gas between the bottom of the axial volume 6 and the annular space occupied by the regenerator 5.
  • the intermediate shell of the cryostat of the invention constituted by the wall 2, is closed at its lower end, at the bottom of the cryostat, by a transverse plate 22 against which the cold exchanger 8 is affixed. On its face opposite this exchanger component 21 is assembled, generally by simple bonding.
  • FIG. 1 therefore shows an electrical distribution ring 23, the conductive parts of which pass through watertight crossings through the external wall of the thermal insulation envelope 1, as well as the conductive wires 24 which connect them then to component 21.
  • the envelope 1 as a whole has the function of limiting the heat losses by radiation or convection at the level of the organs involved in the thermodynamic cycle of the complete cooler in the cold zone thereof.
  • a quality of stainless steel corresponding to an alloy with low thermal conductivity adapted to be compatible with the working gas used, which is preferably helium in the case of the regenerator. with metallic foil rolled up as described below.
  • the outer wall of the casing 1 is also made of stainless steel, or possibly of an appropriate quality of glass, for economic reasons.
  • the base 4 is, on the contrary, in the hot zone of the cooler in operation, where there is also a dynamic pressure of the working gas, subjected to periodic pressure pulses, printed by the mobile elements of the cooler when the cryostat is connected to the casing 50 of an associated pressure oscillator.
  • the base 4 In this hot zone, it is necessary to evacuate the calories of the gas returning from the expansion, after the recovery carried out in the regenerator 5. For this, it is planned to make the base 4 in a material of good conductivity thermal, generally of stainless steel, in a form favoring the losses towards the outside.
  • the base 4 there is a circular flange 16, pierced with holes for the passage of the screws 48 ensuring the attachment to the casing 50 of the cooler, which is connected to bear on the upper face of the flange 16, opposite to the thermal envelope 1.
  • the sealed connection of these two elements (cryostat and pressure oscillator) to the outside is provided by a seal 19, housed in an annular groove on the upper face of the flange 16.
  • the base 4 delivers passage, in the axis of the system, to a central part 10, screwed in a sealed manner in the ring 17, which is internally threaded.
  • a hexagonal groove 41 formed in its upper flat face, is used for its manipulation during assembly.
  • this central part of the cryostat is designed in two different models which, by their external geometry, their dimensioning, and their functional design, are interchangeable in the same cryostat construction.
  • the two models are illustrated in FIG. 1 and in FIG. 2, depending on whether the cryostat 30 is mounted to be coupled with the housings 50 or 60 of one or the other of the two pressure oscillators in the two cooler variants. shown in Figures 6 and 5 respectively.
  • this central part therefore in particular that bearing the reference 10 in FIG. 1, here consists of a single part with the internal tube 3 of the cryostat.
  • this ring forms a distribution ring 71, for the annular distribution of the gas at the head of the regenerator 5. Consequently, this ring is placed above the latter (in the vertical arrangement shown, cryostat under the casing 50), and more precisely at the center of the base 4 in its main part formed by the collar 16.
  • the distribution ring 71 has a circular groove 45, hollowed out in its lower face, which abuts on the regenerator 5. This groove communicates through orifices 46 with an annular chamber 43, extended upwards at 42, which is formed externally in the part of the central part 10 located at the level of the collar 16, between this part and the face opposite the base 4.
  • the central part 10 is shown in FIG. 1 in the model suitable for a TGP type cooler illustrated in FIG. 6.
  • the second model of central part of the cryostat, intended for a Stirling cycle cooler, is shown in the schematic representation in exploded arrangement of FIG. 2.
  • the central part 20 is identical to the previous one externally, but internally, it simply comprises an axial bore 72, formed all along it, with the same diameter as the tube 3, the central volume of which it extends.
  • a channel 11 opens which is drilled axially in the central part 10 to its upper face, where it ends in a calibrated orifice 13 imposing a controlled gas flow.
  • Another pneumatic connection involving one or more channels, is provided through the part 10, with the annular chamber 43 of the gas distribution ring towards the regenerator 5.
  • a calibrated orifice 14 has thus appeared on a channel 12 opening into the axial channel 11.
  • the calibrated orifices of the channels 11-12 function, in a conventional manner in themselves, like valves introducing pneumatic impedances.
  • the main channel 11 thus equipped in operation provides the useful phase shift between the pressure wave generated by the pressure oscillator and the resulting flow variations in the tube containing the pulsed gas.
  • the secondary impedance (channel 12) makes it possible to provide a fraction of the periodic supply flow rate of the tube by withdrawing it directly from the compression outlet, by diverting the circulation passing through the regenerator and the tube. This reduces the thermal load on the regenerator and contributes to improving the efficiency of the cooler, in the case of a pulsed gas cycle.
  • FIG. 1 finally shows an exchanger 9, located in the hot zone in the central volume, at the level of the distribution ring 71.
  • This hot exchanger can optionally be produced in a similar manner to that which will be described below for the cold exchanger, the main thing is that, in this variant embodiment of the cryostat of the invention, it completes the evacuation of the excess calories from the thermodynamic cycle by completing, from the zone hot of the pulsed gas tube, the heat losses to the outside taking place through the base 4, and incidentally from the associated pressure oscillator casing.
  • the thermal regenerator 5 is advantageously constituted, as it appears in FIGS. 1 and 3, so as to fully play its role of thermal accumulator for the recovery taking place, so in itself conventional, between the working gas passing from the compression phase to the expansion phase and the working gas passing from the expansion phase to the compression phase.
  • such a regenerator is in the form of a continuous sheet which is wound in a series of turns around the central tube 3 which limits the internal volume 6 of the regenerator, so as to fill, as completely as is possible in industrial practice, the annular space comprised between this tube 3, which forms its inner shell ferrule, and its associated outer shell ferrule, constituted by the inner wall 2 of the insulating jacket 1.
  • machining processes by photolithography which are known in themselves, are particularly advantageous in this sense, insofar as they represent particularly simple technological means to implement for a limited cost price, when it comes to lead to the configuration illustrated by the detail in FIG. 3.
  • the sheet which is thus wound in contiguous consecutive turns forms a succession of distinct longitudinal bands 27, which are oriented perpendicular to the axis of the cryostat and which are separated from each other by intervals 28.
  • Bars 26 are formed in excess thickness of the strips and across them in a perpendicular direction. They are regularly distributed over the entire length and height of the sheet and staggered, each uniting two successive bands over the gap between them.
  • a regenerator thus constructed, one can cite as an example the case of a sheet 100 to 200 microns thick, hollowed out at mid-thickness by each face, for a regenerator of 2 to 3 millimeters of radial thickness.
  • the strips and the intervals between them can, for example, be of the same width, of the order of 50 to 100 microns.
  • the transverse length of the bars 26 may correspond, here again by way of example, to 1.5 times the repetition pitch of the longitudinal strips 27, with a width approximately half less and a distance between two successive bars offset, equivalent to approximately three times the width of each.
  • the invention thus makes it possible to take advantage of a relationship between the local convective exchange and the losses of longitudinal loads which, in the case of plates parallel to the axis of the cold finger, would be greater than the value which can be obtained by the usual stacks of grids or balls, however, in this practical embodiment, it allows a better distribution of the gas flow between the parallel layers of smooth surfaces.
  • the presence of the barriers 26, which remain small compared to the length and the thickness of the regenerator, also makes it possible to introduce a periodic interruption of the longitudinal flow between the layers of successive strips from one end to the other of the regenerator, and thereby stabilize the overall gas flow. Simultaneously, as these bars adjoin two adjacent layers of strips, we obtain thanks to them a reduction of the losses of thermal energy by conduction in the longitudinal direction. Simultaneously, this ensures a reduction in losses of thermal energy by conduction in the longitudinal direction.
  • regenerator 5 makes it possible, in a particularly advantageous manner in the context of the present invention, to obtain a ratio between the local convective exchange and the very advantageous longitudinal pressure drop, while improving the distribution of the flow rate. gas between the parallel layers oriented longitudinally, until thermal recovery performance at least equivalent, if not greater than that which is known to be obtained in known embodiments by regenerators with stacked transverse grids or with balls.
  • Another characteristic common to the two variants of coolers described here, by way of example, relates to the production of the cold exchanger 8 installed at the bottom of the thermal insulation envelope 1 of the cryostat according to the invention, such as it is more particularly illustrated in FIG. 4.
  • This cold exchanger is produced, in accordance with what emerges from FIGS. 1, 2 and 4, in a so-called daisy shape. It consists of a structure with a geometry of revolution, which is made of a highly conductive material such as copper or aluminum.
  • This structure alternates in a star around a central core 31, empty zones 32 hollowed out through its longitudinal thickness and massive zones 33 ensuring thermal conduction. Both extend radially astride the shoulder 34, on either side of the end of the central tube 3. They therefore allow the gas to circulate freely between the central volume 6 of the cryostat (or at least the expansion chamber remaining at the bottom of the cryostat in the case of a cooler according to FIG. 5 applying a Stirling cycle), bypassing the lower end of the central tube 3 received in the shoulder 34.
  • Such a miniature exchanger for example 5 mm in diameter and 3 mm thick, can be easily manufactured by electrochemical machining of a cylindrical bar, which is then cut into sections.
  • the core 31 can be additionally pierced with an empty passage in its center, and it is not necessary to leave a peripheral crown of material, continuously contiguous with the central tube 3.
  • the massive zones form lobes of material exchanger, again in a configuration straddling the diameter of the tube 3, in which the empty zones between the lobes ensure the passage of gas between the regenerator and either the expansion chamber of a Stirling cycle cooler, the bottom of the gas piston of a pulsed gas tube cooler.
  • FIG. 5 illustrates the combination of the cryostat of the preceding figures, using the central part 20 of FIG. 2, with a pressure oscillator responding to the configuration of a Stirling cycle cooler, in which the control is with a rotary engine.
  • a conventional drive system is schematically represented by a crankshaft 51 whose eccentric is linked to two connecting rods 53, 54, arranged at 90 degrees from one another.
  • the connecting rod 53 is articulated on the end of the displacing piston 55, while the connecting rod 54 is articulated on the compression piston 56 which limits the compression chamber 57.
  • the compressed gas is conveyed by conduits 58, 59 to the channel 39 of the cryostat supplying the distribution chamber 71 of the cryostat, and from there the regenerator 5.
  • the displacer piston 55 is axially movable in the internal volume 6 of the cryostat 30. It occupies almost all of this volume, leaving space at the bottom of the tube 3 which constitutes its guide, only to the thickness of the expansion chamber, considerably enlarged in the figure in relation to practical reality.
  • FIG. 6 uses a pressure oscillator designed for a TGP type cooler, the housing 50 of which is connected to the cryostat around the central part 10 of the model of FIG. 1.
  • control mode is of the rotary type.
  • the engine shaft is perpendicular to the axis of the system and, by an off-center crankshaft 66, it drives in a oscillating movement, a single piston 74.
  • the piston 74 is movable, vertically in the figure, in the axis of the cryostat, in a jacket formed inside the casing 50.
  • the internal cage 68 of a ball bearing On the offset axis 66 is mounted the internal cage 68 of a ball bearing, the external cage 67 of which is trapped in a rectilinear groove 75 hollowed out laterally in the peripheral surface of the piston 74, perpendicular to its axis and to the plane of the figure. This arrangement ensures the reciprocating movement of the piston while immobilizing it in rotation.
  • the compression chamber 63 is formed between the upper end face of the piston and the casing 60. It is connected, as in the previous case, by a bore 62 and a conduit 61 to the channel 39 opening into the distribution chamber of the cryostat .
  • the opposite side of the piston is hollow. There is thus formed, on the side opposite to the compression chamber, a reservoir 65, of large volume relative to the volume of gas in circulation. The pressure prevailing in this tank therefore remains practically constant in operation.
  • the same arrangement can advantageously be applied, leaving the buffer tank directly open on the free surface of the central part 10 at the head of the cryostat, inside the compression piston, in the case of a TGP type cooler whose control is ensured by a linear motor rather than a rotary motor.
  • FIG 7 we have shown a particularly advantageous embodiment for the bottom of the cryostat.
  • the exploded representation used for clarity, schematically shows the regenerator 5 between the tube 3 of pulsed gas and the tubular wall 2, which leaves room for the cold exchanger 8 against the plate 22.
  • the exchanger 8 here consists of lobes 77 of solid material in radiating arrangement around a central core 34. Between these lobes 77 are located the gas passages 78 which make the lower end of the regenerator communicate with the axial volume of the tube 3.
  • the laminate for tranquilizing the gas flow which has already been discussed, is represented by a stack of perforated grids 81 mounted in cross section of the tube 3 at this lower end. These grids can be retained by lugs of the tube 3, as shown, or simply wedged between the end of the tube and the exchanger 8 in its central part limited by a shoulder 79 for centering the tube 3. In all cases, the gas passing between the exchanger lobes is found to have to pass through the stack of grids.
  • This circulation is indicated by arrows in FIG. 8, which relates to another particularly advantageous embodiment in particular in that it facilitates a tranquilization of the gas flow as close as possible to the cold plate 22.
  • the cold exchanger is produced therein.
  • two parts 83 and 84 nested concentrically one inside the other; Each has its own lobes of heat exchange material alternating with empty areas free for gas circulation.
  • the exchanger is therefore pierced with channels dividing into two rings, one under the regenerator 5, the other at the end of the tube 3.
  • the internal part 83 of the exchanger is more shorter than the external part 84 which surrounds it and so that the end of the tube 3 is centered in the part 84 abutting on the part 83.
  • a stack of grids 82 constitutes the laminate for tranquilizing the gas flow. These grids are interposed directly against the cold plate 22 between the latter and the two parts 83 and 84 of the exchanger. If necessary, they could be blocked in the exchanger at the periphery, providing for this purpose a shoulder in the part 84 forming the annular ring of this exchanger.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
EP19970400898 1996-04-23 1997-04-22 Kryostat für Tiefsttemperatur-Kälteanlage und Kälteanlagen mit einem solchen Kryostat Expired - Lifetime EP0803687B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9605086A FR2747767B1 (fr) 1996-04-23 1996-04-23 Cryostat pour refroidisseur cryogenique et refroidisseurs comportant un tel cryostat
FR9605086 1996-04-23

Publications (2)

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EP0803687A1 true EP0803687A1 (de) 1997-10-29
EP0803687B1 EP0803687B1 (de) 2002-06-26

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EP19970400898 Expired - Lifetime EP0803687B1 (de) 1996-04-23 1997-04-22 Kryostat für Tiefsttemperatur-Kälteanlage und Kälteanlagen mit einem solchen Kryostat

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EP (1) EP0803687B1 (de)
DE (1) DE69713547T2 (de)
FR (1) FR2747767B1 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2815700A1 (fr) * 2000-10-19 2002-04-26 Sagem Dispositif cryogenique a cycle ferme
FR2821150A1 (fr) * 2001-02-17 2002-08-23 Lg Electronics Inc Refregirateur a tube pulse
EP1251320A4 (de) * 1999-12-21 2004-03-24 Sharp Kk Stirling-kältemaschine
WO2012012785A1 (en) * 2010-07-22 2012-01-26 Flir Systems, Inc. Expander for stirling engines and cryogenic coolers
EP2767781A1 (de) * 2013-02-19 2014-08-20 The Hymatic Engineering Company Limited Impulsröhrenkühlschrank/Kryokühlervorrichtung
CN118129389A (zh) * 2024-05-07 2024-06-04 上海量羲技术有限公司 一种稀释制冷装置

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US3220201A (en) * 1965-01-25 1965-11-30 Little Inc A Cryogenic refrigerator operating on the stirling cycle
US3851173A (en) * 1973-06-25 1974-11-26 Texas Instruments Inc Thermal energy receiver
US4425764A (en) * 1982-03-16 1984-01-17 Kryovacs Scientific Corporation Micro-cryogenic system with pseudo two stage cold finger, stationary regenerative material, and pre-cooling of the working fluid
US4550571A (en) * 1983-12-28 1985-11-05 Helix Technology Corporation Balanced integral Stirling cryogenic refrigerator
US4569203A (en) * 1984-10-29 1986-02-11 Texas Instruments Incorporated Cryogenic cooler
US4858442A (en) * 1988-04-29 1989-08-22 Inframetrics, Incorporated Miniature integral stirling cryocooler
EP0339298A1 (de) * 1988-04-14 1989-11-02 Leybold Aktiengesellschaft Verfahren zur Herstellung eines Regenerators für eine Tieftemperatur-Kältemaschine und nach diesem Verfahren hergestellter Regenerator
EP0576202A1 (de) * 1992-06-24 1993-12-29 Gec-Marconi Limited Kühler
US5293748A (en) * 1990-07-10 1994-03-15 Carrier Corporation Piston cylinder arrangement for an integral Stirling cryocooler
EP0614059A1 (de) * 1993-03-02 1994-09-07 Cryotechnologies Kühler mit einem Schwingrohrkaltkopf
US5435136A (en) * 1991-10-15 1995-07-25 Aisin Seiki Kabushiki Kaisha Pulse tube heat engine
EP0717245A2 (de) * 1994-12-12 1996-06-19 Hughes Aircraft Company Konzentrischer Stossrohrentspanner

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Publication number Priority date Publication date Assignee Title
US3220201A (en) * 1965-01-25 1965-11-30 Little Inc A Cryogenic refrigerator operating on the stirling cycle
US3851173A (en) * 1973-06-25 1974-11-26 Texas Instruments Inc Thermal energy receiver
US4425764A (en) * 1982-03-16 1984-01-17 Kryovacs Scientific Corporation Micro-cryogenic system with pseudo two stage cold finger, stationary regenerative material, and pre-cooling of the working fluid
US4550571A (en) * 1983-12-28 1985-11-05 Helix Technology Corporation Balanced integral Stirling cryogenic refrigerator
US4569203A (en) * 1984-10-29 1986-02-11 Texas Instruments Incorporated Cryogenic cooler
EP0339298A1 (de) * 1988-04-14 1989-11-02 Leybold Aktiengesellschaft Verfahren zur Herstellung eines Regenerators für eine Tieftemperatur-Kältemaschine und nach diesem Verfahren hergestellter Regenerator
US4858442A (en) * 1988-04-29 1989-08-22 Inframetrics, Incorporated Miniature integral stirling cryocooler
US5293748A (en) * 1990-07-10 1994-03-15 Carrier Corporation Piston cylinder arrangement for an integral Stirling cryocooler
US5435136A (en) * 1991-10-15 1995-07-25 Aisin Seiki Kabushiki Kaisha Pulse tube heat engine
EP0576202A1 (de) * 1992-06-24 1993-12-29 Gec-Marconi Limited Kühler
EP0614059A1 (de) * 1993-03-02 1994-09-07 Cryotechnologies Kühler mit einem Schwingrohrkaltkopf
EP0717245A2 (de) * 1994-12-12 1996-06-19 Hughes Aircraft Company Konzentrischer Stossrohrentspanner

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1251320A4 (de) * 1999-12-21 2004-03-24 Sharp Kk Stirling-kältemaschine
FR2815700A1 (fr) * 2000-10-19 2002-04-26 Sagem Dispositif cryogenique a cycle ferme
FR2821150A1 (fr) * 2001-02-17 2002-08-23 Lg Electronics Inc Refregirateur a tube pulse
WO2012012785A1 (en) * 2010-07-22 2012-01-26 Flir Systems, Inc. Expander for stirling engines and cryogenic coolers
US8910486B2 (en) 2010-07-22 2014-12-16 Flir Systems, Inc. Expander for stirling engines and cryogenic coolers
EP2767781A1 (de) * 2013-02-19 2014-08-20 The Hymatic Engineering Company Limited Impulsröhrenkühlschrank/Kryokühlervorrichtung
GB2524893A (en) * 2013-02-19 2015-10-07 Hymatic Eng Co Ltd A pulse tube refrigerator / cryocooler apparatus
US9909787B2 (en) * 2013-02-19 2018-03-06 The Hymatic Engineering Company Limited Pulse tube refrigerator/cryocooler apparatus
GB2510912B (en) * 2013-02-19 2018-09-26 The Hymatic Engineering Company Ltd A pulse tube refrigerator / cryocooler apparatus
GB2524893B (en) * 2013-02-19 2018-11-28 The Hymatic Engineering Company Ltd A gas flow distribution device for distributing gas to a regenerator of a pulse tube refrigerator cryocooler apparatus
CN118129389A (zh) * 2024-05-07 2024-06-04 上海量羲技术有限公司 一种稀释制冷装置

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FR2747767A1 (fr) 1997-10-24
FR2747767B1 (fr) 1998-08-28
DE69713547D1 (de) 2002-08-01
EP0803687B1 (de) 2002-06-26
DE69713547T2 (de) 2003-01-16

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