EP0778452A1 - Stirling-Kühlanlage mit Drehantrieb - Google Patents

Stirling-Kühlanlage mit Drehantrieb Download PDF

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Publication number
EP0778452A1
EP0778452A1 EP96402620A EP96402620A EP0778452A1 EP 0778452 A1 EP0778452 A1 EP 0778452A1 EP 96402620 A EP96402620 A EP 96402620A EP 96402620 A EP96402620 A EP 96402620A EP 0778452 A1 EP0778452 A1 EP 0778452A1
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EP
European Patent Office
Prior art keywords
piston
cooler according
eccentric
tube
connecting element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP96402620A
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English (en)
French (fr)
Inventor
Patrick THOMSON-CSF SCPI Curlier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Cryotechnologies SA
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Cryotechnologies SA
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Filing date
Publication date
Application filed by Cryotechnologies SA filed Critical Cryotechnologies SA
Publication of EP0778452A1 publication Critical patent/EP0778452A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/34—Ultra-small engines, e.g. for driving models
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
    • F02G2243/30—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/08—Thermoplastics

Definitions

  • the present invention relates to a Stirling cycle cooler of the type comprising means with rotary piloting of phase shifted translation drive for a compression piston limiting a compression chamber and a displacing piston limiting a expansion chamber and constituting regenerative exchanger on a circuit for circulating a thermodynamic fluid in a closed circuit between said chambers.
  • coolers which use a reversible thermodynamic cycle called Stirling, consisting in subjecting a thermodynamic working fluid to a compression phase at hot temperature. and an expansion phase at cold temperature, separated by two intermediate phases where, theoretically at constant volume, the fluid passes through a regenerative material which captures the specific cooling energy of the cold fluid leaving the expansion phase to restore it to the hot fluid at its return from the compression phase to the expansion phase.
  • Stirling a reversible thermodynamic cycle
  • cryogenic coolers include a closed circuit of thermodynamic fluid, generally a high purity gas such as helium, between a compression chamber at hot temperature whose volume is variable under the control of 'a pressure oscillator, and an expansion chamber at cold temperature delivering to the component to cool the cooling power released by the expansion of the thermodynamic fluid. Between these two chambers, both in the forward direction and in the return direction, the circuit is at least partially constituted by a regenerator which is produced in the form of an elongated tube containing the regenerating material.
  • thermodynamic fluid generally a high purity gas such as helium
  • this regenerator is generally itself mobile at the limit of the volume of the expansion chamber, the notion of its movement often takes precedence over its function of regenerator in terminology, which leads to designate it by the terms of tube or displacement piston, or displacement exchanger. It nevertheless retains its primary function of being traversed by the fluid during heating or cooling, in theory excluding expansion and compression, by the fact that its movements are out of phase with respect to changes in the volume of the chamber. pressure oscillator hot. However, it also plays an important role in regulating the thermodynamic cycle through the pressure drop it implies.
  • the present invention provides improvement to those which, more precisely, are embodied in monoblock systems, where rotary type motor means which serve to drive in translation a compression piston limiting the hot temperature chamber in the 'pressure oscillator, also control the movements of the regenerator, in translation in a cryostatic well terminated by the expansion chamber at cold temperature from where the frigories produced are transmitted to the element to be cooled.
  • the invention aims in particular to reduce the manufacturing costs and to improve the operating conditions of such Stirling cycle and rotary pilot coolers common to the compression piston and the regenerative displacer piston.
  • it makes it possible in particular to increase safety and the service life, in particular by reducing the number mechanical connections with fragile joints, to limit the risks of contamination of the thermodynamic fluid and fouling of the circuit which it borrows, to facilitate the synchronization and the time shift of the four thermodynamic phases of the cycle.
  • the invention therefore essentially relates to a Stirling cycle cooler of the type comprising means with rotary piloting of phase shifted translation drive for a compression piston limiting a compression chamber and a displacing piston limiting a expansion chamber and constituting regenerative exchanger on a circuit for circulating a thermodynamic fluid in a closed circuit between said chambers, in which the drive means comprise a mechanical connection element of the two pistons with each other which is guided linearly around a mechanism eccentric mounted off-center on a rotary drive shaft, in an intermediate middle part between two between two lateral branches terminated by attachment points on each of said pistons respectively.
  • this element is a non-compressible flexible tube also constituting a conduit for circulation of the thermodynamic working fluid between the compression chamber and an inlet end in the displacer tube opposite a cold end limiting the relaxation room. Said element then combines the mechanical connection and pneumatic connection functions.
  • such an element is structured and configured in such a way that it fulfills a spring function which advantageously combines with its mechanical connection function, and preferably also its pneumatic connection function.
  • this mechanism advantageously comprises a semi-circular holding and guiding cage which is mounted on a crankshaft eccentric having a groove in which the piston-to-piston connecting element is engaged, and that such a cage is advantageously of semi-circular shape, in order to tighten said element in its receiving groove only on a part of the periphery of the eccentric, where it does not have to play with flexibility during the operating cycle and where it is desirable that a central point of its middle part is stuck in a fixed position on the eccentric.
  • the mechanical connection element between the two pistons preferably produced in the form of a conductive tube of the thermodynamic working fluid, is advantageously claimed by a natural open configuration of its middle part. before mounting on the eccentric, and that it thus succeeds in limiting the mechanical stresses generated by the rotary piloting of the pistons, and in particular, in balancing the radial forces imposed by the compression piston on its jacket in its dynamic displacement and thus significantly reducing the effects of selective wear on the walls of the jacket of the compressor piston.
  • its spring function preferably involves two curvatures which it forms in its lateral branches, each with a concavity in the opposite direction to that of its median part around the eccentric, so as to maintain each branch in axial alignment with the piston corresponding to the vicinity of the attachment point.
  • coolers of the rotary pilot type following a Stirling thermodynamic cycle are already known. They are preferably produced in miniature and monobloc form to be used for the cryogenic cooling of electronic components, although they can also be used in other fields, like all those which involve superconductors having to be maintained at cryogenic temperature.
  • FIG. 14 A known embodiment of a one-piece miniature Stirling cooler with rotary engine and integrated cold probe is described in particular in the French publication entitled “Engineering Techniques, Electronic Treaty” by Damien FEGER, on pages numbered E4070 n ° 1 to 11.
  • the concept of a low-cost rotary Stirling cooler is notably represented in FIG. 14, where one clearly sees a crankshaft which drives the compression piston and the piston porous displacer, or regenerator, by means of two rigid and independent rods, articulated at their two ends, which are arranged at 90 degrees from each other.
  • the cooler described here differs essentially from the previous one in that the mechanical drive of the compression piston, as well as the mechanical drive of the porous displacing piston, are carried out by means of a single and unique element.
  • link linearly disposed between the compression piston and the inlet of the displacing piston, while being driven by means of an eccentric mechanism similar to a crankshaft.
  • the mechanical connection is combined with the pneumatic connection necessary for the circulation of the working fluid.
  • the linear element is a flexible and non-extensible, but also non-compressible tube, which conducts the thermodynamic fluid between the compression chamber limited by the compression piston and the inlet of the displacing piston in regenerative material which it crosses between this inlet and the cold end of this piston limiting the expansion chamber. It is therefore no longer necessary to drill holes in the cooler housing to make the compression chamber communicate with the entry of the displacing piston, a hole that can be seen clearly on the cooler of the prior art shown by the figure 14 mentioned above.
  • FIG. 1 of the drawings here appended there are recognized elements known for themselves of existing rotary piloted Stirling coolers, namely a casing 2, enclosing a pressure oscillator which ensures the compression of the thermodynamic fluid at each operating cycle by a compression piston 3, a displacement piston 5 of elongated shape, movable in translation in a guide tube 55 outside the pressure oscillator, and a crankshaft mechanism whose eccentric 4 is rotatably mounted, but in the off center position, on a motor shaft 6, centered on the axis of the internal cylindrical volume of the casing 2.
  • the shaft 6 is used both to drive the compression piston 3 in translation and to control the translational movements of the displacing piston 5.
  • the two pistons 3 and 5 are movable in radial directions of the volume internal cylindrical of the casing 2, but angularly offset from each other by 90 degrees, in order to ensure the desired phase shift between the stages of the thermodynamic cycle.
  • the pressure oscillator is provided with lugs 22 at the periphery of the casing 2, which are intended for mounting the cooler by fixing on a support (not shown).
  • the compression piston 3 limits a compression chamber 23 of the thermodynamic fluid at the bottom of a fixed jacket 26 for guiding the piston constituting both the cylinder head 29 of the compressor and the closure plug for a radial connection 24 of the casing 2.
  • the displacement piston 5 extends between an inlet end 51 located in the hot zone on the side of the oscillator pressure and a cold end 53 located at the opposite end, where an expansion chamber 13 is formed.
  • its guide tube 55 ends with a cold plate 52 for mounting a component to be cooled 54, affixed against the cold end so as to best receive, by thermal conduction, the cooling capacity produced by the expansion of the working fluid.
  • the displacing piston 5 and its guide tube 55 together constitute what is commonly called a cold finger, and this piston plays the role of thermal regenerator, being filled with a porous material suitably chosen to this effect, generally consisting of a stack of metal grids inside a thermal insulating tube.
  • the component to be cooled 54 is, for example, an infrared detector. A space is maintained between the cold plate which supports it and the tip of the cold finger, in order to avoid the transmission of vibrations.
  • the cold finger is completely surrounded by a thermal insulation envelope 59, with a double wall under vacuum, which is only mentioned in the figure. It is connected, generally by welding or gluing, to the radial nozzle 25 at its hot zone 51. This produces the one-piece construction of the cooler recommended by the invention and in accordance with the concept of integrated cold probe, the cold finger representing a well cryostat.
  • the expansion chamber 13 is reduced to its minimum volume, the cold end of the displacer piston 5 being at the end of its travel towards the component to be cooled at the bottom of the guide tube 55.
  • the compression piston 3 is, on the contrary, distant from the cylinder head 29 at the bottom of its jacket 26 at the level of the compression chamber 23. The position is that of the operating phase described below with reference to FIG. 5d.
  • the drive of the compression piston 3 and of the porous displacing piston 5 from the movement of the crankshaft eccentric 4 is effected by means of a connecting element 35 which, in the present case, is more particularly a connecting tube 35 for ensuring both the mechanical connection and the pneumatic connection between the two pistons.
  • This connecting tube 35 is fixed at each end, by brazing or welding between metal parts, on the one hand with the compression piston 3 and on the other hand with the porous displacing piston 5, more precisely with the channel 58 which admits the pressure modulation in the porous regenerative material contained in the displacing piston, and there by means of a miniature bellows with low stiffness 69.
  • the connecting tube 35 is of circular or ovoid section which remains constant, over a non-extendable length, while it has the flexibility necessary to deform each revolution of the axis of the eccentric 4, bending elastically between the eccentric and each of its ends 74, 75 terminated by its attachment points on the two pistons.
  • each of the fixings at these attachment points is preferably carried out as far as possible from the axis of the crankshaft, in order to reduce the radial forces of the pistons on their liners and to lengthen the service life of leak tightness.
  • the piston 3 is hollow and the tube 35 is fixed on it (at 77, FIG. 1) on the side of the compression chamber 23, flush with its cap and beyond. an empty annular space 33 internal to the piston. This design provides the equivalent of a large length of rod without interfering with lateral travel.
  • Figure 2 being in section along a diametrical plane of the pressure oscillator, it shows a housing 11 in extension of the housing 2 which encloses the electric motor 10 driving the shaft 6 of the cooler, with its stator 12 and its rotor 14.
  • the crankshaft 6, constituted by the axis of the rotor, is rotatably mounted on ball bearings and it is provided with a flywheel 15 which makes it possible to optimize the shape of the mechanical torque required by the cooler and thereby reduce power consumption.
  • the motor casing 11 is integral with the casing 2 by a connection between their respective walls which is impermeable to the working gas filling the internal volume.
  • the stator's electrical winding is therefore isolated by an organic resin with low degassing of impurities which would pollute the working gas.
  • crankshaft mechanism The constitution of the crankshaft mechanism is shown in Figures 1,2 and 3.
  • the eccentric 4 is cantilevered at the end of the shaft 6, on an axis 61, which is in practice of reduced section as in FIG. 2 and 3.
  • the body of the eccentric 4 is made of an annular ring 42 in which is engaged by force the outer cage of a miniature ball bearing system 62 mounted sliding on the axis 61 by its inner cage.
  • the use of a pair of mounted twin bearings as illustrated can reduce the rolling torque.
  • the ball bearing 17 supporting the shaft 6 on the motor housing 6 on this side is split in the same way.
  • the ring 42 is started by a circular groove 43 in which the connecting tube 35 is housed.
  • the latter is partially enclosed therein and held by means of a cage 44 which forms a semi-circular ring.
  • a cage 44 which forms a semi-circular ring.
  • the cage 44 has an internally flared periphery towards the edges of its semi-circular shape, such as 45, which has the consequence that it leaves the tube 35 more free to deform during its drive by the crankshaft mechanism.
  • FIGS. 5a to 5d clearly show how the engine movement is transmitted by the crankshaft and the tube 35 to the pistons 3 and 5 so as to ensure the four phases of a Stirling cycle
  • FIG. 4 represents the configuration presented by the tube 35 naturally, before mounting around the eccentric and fixing to the pistons.
  • the geometric shape chosen is particularly well suited for the tube 35 to provide the desired spring effect according to the invention.
  • the tube 35 breaks down into three parts in its linear configuration.
  • a middle part 71 which forms an arc intended to fit on the eccentric on either side of the fixed central point already mentioned.
  • This middle part is intermediate between two lateral branches 72 and 73, each of which ends in a straight end 74 or 75 towards the point of attachment to the corresponding piston.
  • the spring tube 35 is mounted pretended on the eccentric 4 from a natural curvature of its middle part 71 whose angular opening is greater than that of the eccentric, therefore less concave than that of the cage 44 which maintains it in the groove of the latter, as it appears in FIG. 4.
  • This is how we ensure, during operation, a pretensioning effect which tends to open the angle of 90 degrees between the axes of the pistons, and which contributes to keeping the tube 35 in alignment with the axes of the pistons in the vicinity of the respective attachment points, by virtue of an initial flexibility constraint which is balanced in dynamics.
  • the advantage of this arrangement is particularly noticeable in the case of the compressor piston, since it results in a considerable reduction in selective wear on a preferential generator of his shirt that we deplore in the coolers previously designed.
  • the middle part 71 extends over a length which corresponds substantially to that of a semicircle around the eccentric, and that the two lateral branches 72 and 73 which are made for move away from it to the pistons at the ends of the tube 35, themselves form convex bumps, in curves whose concavity is turned in the opposite direction to that of the middle part 71, before joining the rectilinear shape that 'they have at their ends 74, 75, in the immediate vicinity of the points of attachment to their respective pistons.
  • the tube 35 behaves in practice as a linear mechanical connecting element having the properties of a spring with high stiffness and that its deformations best follow those which correspond to a linear translation of the pistons.
  • the bellows 69 advantageously made of stainless steel like the connecting tube itself, is easily capable of containing the dynamics of pneumatic pressure, insofar as it is located in the internal volume of the casing 2, and therefore subject externally at loading pressure.
  • it will however be preferable to replace such a bellows connection with a ball joint mounting of the end of the tube 35 in the body of the displacer, more precisely in its interface part 78, including the channel 58 remains in communication through the ball joint with the tube 35 for the passage of the working gas.
  • FIGS. 5a to 5d This is illustrated by FIGS. 5a to 5d, in which it has been sought to show both the deformations of the curves of the tube 35 and the displacement of its points of attachment to the pistons at its opposite ends, schematically representing the assembly for four typical positions during a cycle. Note, however, that the representation remains theoretical in relation to what continuous rotation can give in practical reality.
  • the end linked to the compression piston passes from the position A1 for maximum reduction of the compression volume to the position A3 at the end of compression (FIG. 5c) passing through the intermediate quarter-cycle position A2. It then returns to position A1 in FIG. 5a passing substantially through the same intermediate position A2 in FIG. 5d.
  • the end linked to the displacing piston starts from an intermediate position B1 (FIG. 5a) to come to its retracted position B2 corresponding to a maximum volume of the expansion chamber (FIG. 5b), then it returns to the position B1 (FIG. 5c) before reaching towards position B3 in FIG. 5d, corresponding to the minimum volume of the expansion chamber.
  • the middle part of the spring tube 35 bears partly on the bottom of the groove 43, but also on the guide cage 44 itself, taking into account its flared edges and the pretension of the tube.
  • the efforts are exerted mainly on the side of the lateral branch attached to the compression piston, where moreover, the problem of axial alignment is less posed, for this reason, the curvature of the convex bump of the tube of this side was made knowingly more inflated in amplitude than that of the side of the displacer piston.
  • the thrust axes are shown diagrammatically by the lines X1, X2, X3 passing through the center of the axis of the eccentric.
  • helium is used as the working gas in known coolers, but for operation at intermediate cold temperatures, of the order of 120 to 150 ° K, it is better here to use air, nitrogen, argon, or preferably neon.
  • the tube 35 is made of a steel of good ductility in stainless quality, such as type Z10, steel. semi-hard annealing. It is implemented in a circular section pipe.
  • the tube 35 may, for example, have a linear length of 44 mm, for a mobility of its ends over a distance of the order of 1 mm, and a passage section equivalent to that of a circular diameter of 1.5 mm under a wall thickness of 150 microns.
  • the respective diameters of the two pistons are for example 6 mm for a displacing piston offering a regenerator length of 41 mm, and 14 mm for the compression piston.
  • the main casing 2, the engine casing 11 and the guide tube 55 of the displacing piston together constitute a tight monolithic enclosure for the working gas, which fills its internal volume under the static loading pressure.
  • this enclosure are located all the movable elements of the cooler of the invention. With a view especially to low cost, it can be made of plastic of the technical type. Its different parts are manufactured by molding and assembled with a tight connection of the walls by gluing. If one adds a surface metallization on the internal side, one avoids the consequences of a potential degassing of the organic constituents and the phenomenon of hygroscopicity.
  • a material of good mechanical strength with high thermal conductivity is used in order to ensure the rejection of the heat of compression to the outside.
  • the same material may be suitable for the crankcase for the same reasons, especially if it has its own insulating properties to facilitate watertight electrical crossings.
  • the heat rejection can be further improved if it is planned to keep the choice of a metallic material (stainless steel) for the cylinder head 29 of the compressor and the jacket 26 of the compression piston, made in one piece, the piston compression 3 itself being metallic in nature.
  • the dynamic seal between the compression piston and its jacket is provided for example by a coating of polytetrafluoroethylene preferably impregnated with a sliding additive to reduce the coefficient of friction between piston and jacket.
  • a coating of polytetrafluoroethylene preferably impregnated with a sliding additive to reduce the coefficient of friction between piston and jacket.
  • the same type of coating can be applied to the displacement piston to facilitate its sliding, especially in its part mounted on the compressor housing.
  • a plastic material based on the same resins as the casing or compatible resins can moreover be used for the tube 55 for guiding the displacing piston, with the proviso that it is desirable for it to be thermally insulating, as indeed the tube forming the clean wall of the displacing piston and that it is impermeable to the working gas.
  • the thermal insulation envelope of the cold finger does not strictly need to be under vacuum, and a filling of gas blanketing in a double wall of plastic may be appropriate.
  • the interface piece 78 of the displacing piston is of cylindrical shape, and it is bonded in the tube specific to the displacer for sealing in static pressure which is here sufficient. Indeed, as the working gas is forced through the porous regenerator along its axis by the pressure modulation conducted by the tube 35 located in the pressurized volume internal to the casing 2, there is no longer any need for the static sealing which previously required the bores through the casing which made the fluid enter laterally into the displacer tube from the compression chamber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
EP96402620A 1995-12-08 1996-12-04 Stirling-Kühlanlage mit Drehantrieb Withdrawn EP0778452A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9514545 1995-12-08
FR9514545A FR2742215B1 (fr) 1995-12-08 1995-12-08 Refroidisseur stirling a pilotage rotatif

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EP0778452A1 true EP0778452A1 (de) 1997-06-11

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FR (1) FR2742215B1 (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7555908B2 (en) 2006-05-12 2009-07-07 Flir Systems, Inc. Cable drive mechanism for self tuning refrigeration gas expander
US7587896B2 (en) 2006-05-12 2009-09-15 Flir Systems, Inc. Cooled infrared sensor assembly with compact configuration
US8074457B2 (en) 2006-05-12 2011-12-13 Flir Systems, Inc. Folded cryocooler design
US8959929B2 (en) 2006-05-12 2015-02-24 Flir Systems Inc. Miniaturized gas refrigeration device with two or more thermal regenerator sections
FR3033629A1 (fr) * 2015-03-13 2016-09-16 Thales Sa Refroidisseur stirling a transfert de fluide par conduit deformable
KR20170126917A (ko) * 2015-03-13 2017-11-20 탈레스 플렉시블 재생기 구동장치를 구비하는 스털링 쿨러
EP3674626A1 (de) * 2018-12-28 2020-07-01 Thales Kühlvorrichtung mit stirlingzyklus und monoblockhalterung
US10989446B2 (en) * 2017-06-30 2021-04-27 Safran Electronics & Defense Cooling device intended to equip an infrared vision device with a deformable element

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US3222877A (en) * 1964-01-22 1965-12-14 Frank P Brooks Low temperature refrigerator
US3552120A (en) * 1969-03-05 1971-01-05 Research Corp Stirling cycle type thermal device
US4078389A (en) * 1976-04-30 1978-03-14 Cryogenic Technology, Inc. Lost-motion refrigeration drive system
US4143520A (en) * 1977-12-23 1979-03-13 The United States Of America As Represented By The Secretary Of The Navy Cryogenic refrigeration system
US4330992A (en) * 1980-04-11 1982-05-25 Sunpower, Inc. Drive mechanism for Stirling engine displacer and other reciprocating bodies
US4353683A (en) * 1980-04-21 1982-10-12 Clark Earl A Stirling cycle engine and fluid pump

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3222877A (en) * 1964-01-22 1965-12-14 Frank P Brooks Low temperature refrigerator
US3552120A (en) * 1969-03-05 1971-01-05 Research Corp Stirling cycle type thermal device
US4078389A (en) * 1976-04-30 1978-03-14 Cryogenic Technology, Inc. Lost-motion refrigeration drive system
US4143520A (en) * 1977-12-23 1979-03-13 The United States Of America As Represented By The Secretary Of The Navy Cryogenic refrigeration system
US4330992A (en) * 1980-04-11 1982-05-25 Sunpower, Inc. Drive mechanism for Stirling engine displacer and other reciprocating bodies
US4353683A (en) * 1980-04-21 1982-10-12 Clark Earl A Stirling cycle engine and fluid pump

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7555908B2 (en) 2006-05-12 2009-07-07 Flir Systems, Inc. Cable drive mechanism for self tuning refrigeration gas expander
US7587896B2 (en) 2006-05-12 2009-09-15 Flir Systems, Inc. Cooled infrared sensor assembly with compact configuration
US8074457B2 (en) 2006-05-12 2011-12-13 Flir Systems, Inc. Folded cryocooler design
US8959929B2 (en) 2006-05-12 2015-02-24 Flir Systems Inc. Miniaturized gas refrigeration device with two or more thermal regenerator sections
CN107407509A (zh) * 2015-03-13 2017-11-28 泰雷兹公司 通过可变形导管进行流体输送的斯特林制冷机
WO2016146572A1 (fr) * 2015-03-13 2016-09-22 Thales Refroidisseur stirling à transfert de fluide par conduit déformable
KR20170126917A (ko) * 2015-03-13 2017-11-20 탈레스 플렉시블 재생기 구동장치를 구비하는 스털링 쿨러
KR20170126923A (ko) * 2015-03-13 2017-11-20 탈레스 변형 가능한 도관에 의한 유체 전달을 구비하는 스털링 쿨러
FR3033629A1 (fr) * 2015-03-13 2016-09-16 Thales Sa Refroidisseur stirling a transfert de fluide par conduit deformable
US20180058731A1 (en) * 2015-03-13 2018-03-01 Thales Stirling cooler with fluid transfer by deformable conduit
CN107407509B (zh) * 2015-03-13 2019-10-08 泰雷兹公司 通过可变形导管进行流体输送的斯特林制冷机
US10465947B2 (en) 2015-03-13 2019-11-05 Thales Stirling cooler with fluid transfer by deformable conduit
KR102443431B1 (ko) 2015-03-13 2022-09-15 탈레스 플렉시블 재생기 구동장치를 구비하는 스털링 쿨러
US10989446B2 (en) * 2017-06-30 2021-04-27 Safran Electronics & Defense Cooling device intended to equip an infrared vision device with a deformable element
EP3674626A1 (de) * 2018-12-28 2020-07-01 Thales Kühlvorrichtung mit stirlingzyklus und monoblockhalterung
FR3091338A1 (fr) * 2018-12-28 2020-07-03 Thales Dispositif de refroidissement à cycle Stirling inversé avec support monobloc
US11473815B2 (en) 2018-12-28 2022-10-18 Thales Stirling-cycle cooling device with monobloc support

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FR2742215B1 (fr) 1998-01-02
FR2742215A1 (fr) 1997-06-13

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