EP3217137A1 - Vorrichtung zur thermischen kühlung eines objekts mithilfe einer kühlquelle, wie etwa einem kühlmittelbad - Google Patents

Vorrichtung zur thermischen kühlung eines objekts mithilfe einer kühlquelle, wie etwa einem kühlmittelbad Download PDF

Info

Publication number
EP3217137A1
EP3217137A1 EP17160161.0A EP17160161A EP3217137A1 EP 3217137 A1 EP3217137 A1 EP 3217137A1 EP 17160161 A EP17160161 A EP 17160161A EP 3217137 A1 EP3217137 A1 EP 3217137A1
Authority
EP
European Patent Office
Prior art keywords
heat exchange
fins
fin
exchange element
cold source
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Withdrawn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
EP17160161.0A
Other languages
English (en)
French (fr)
Inventor
Jérôme Andre
Florian BANCEL
Jean-Marc Poncet
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.)
Commissariat a lEnergie Atomique et aux Energies Alternatives CEA
Original Assignee
Commissariat a lEnergie Atomique et aux Energies Alternatives CEA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Commissariat a lEnergie Atomique et aux Energies Alternatives CEA filed Critical Commissariat a lEnergie Atomique et aux Energies Alternatives CEA
Publication of EP3217137A1 publication Critical patent/EP3217137A1/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/006—Thermal coupling structure or interface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F2013/005—Thermal joints
    • F28F2013/008—Variable conductance materials; Thermal switches

Definitions

  • the invention relates to a device for thermal cooling of an object constituting a hot source, from a cold source such as a bath of cryogenic fluid.
  • a known solution In order to obtain a stable cryogenic temperature, a known solution relies on the use of a saturation bath containing a saturated cryogenic fluid (for example helium), in liquid form, acting as a cold source.
  • a saturated cryogenic fluid for example helium
  • the temperature of the saturation bath is set by the nature of the fluid and its pressure. For a given pressure, the temperature of the cryogenic bath is fixed. From this saturation bath, an object can be cooled to a temperature close to that of the bath. For example, one can immerse the object in the bath, entirely or partially. The heat received by the object is evacuated by evaporation of the bath fluid.
  • This solution is, however, not very flexible because it is limited to cooling at a temperature close to that of the bath, which is fixed by the nature of the fluid and its pressure.
  • a first solution consists in placing a thermal resistance between the fluid bath (cold source) and the object to be cooled (hot source).
  • the thermal resistance makes it possible to evacuate the heat of the object and to obtain a controlled temperature difference between the bath and the object to be cooled.
  • this solution has the disadvantage of significantly increasing the cryogenic fluid consumption when one seeks to obtain a temperature which is away from that of the bath.
  • a second solution is based on the use of a natural convection cell within which the gas density is varied to vary the thermal conductance. This solution is however not satisfactory because the variation in gas density is difficult to master, particularly in the vicinity of the critical and two-phase conditions of the exchange gas, and the behavior of the fluid is particularly unstable due to the natural convection phenomenon.
  • thermo gas switches to establish or remove (or almost eliminate), at will, a thermal connection between two parts.
  • the document WO2007 / 147981 describes an example of a gas thermal switch.
  • the performance of such a thermal switch depends in particular on its cutoff ratio. This parameter corresponds to the ratio of the maximum thermal conductance of the switch (corresponding to the ON or "closed” position of the switch) on the minimum thermal conductance of the switch (corresponding to the OFF or "open” position of the switch. 'light switch).
  • This type of switch comprising simple workpieces, is used for small refrigerating powers.
  • the present invention improves the situation.
  • the architecture of the cooling device of the invention is close to that of a thermal switch with an exchange gas, as described in the document US 2005/0230097 , adapted for heat exchanges of low power typically between 0.01 W and 0.3 W. It differs in particular in that it comprises wedges positioning or centering fins. The presence of these wedges degrades the cutoff ratio of the device. Their use is therefore a priori not desirable within such a device.
  • the structure of a standard thermal switch is modified by adding wedges positioning or centering fins, which increases the size of the device and divert the use to ensure the thermal cooling of an object with a higher exchanged thermal power level, up to several watts.
  • the cooling device comprises an element for adjusting the heat exchange gas pressure in the enclosure or a pump for introducing and extracting heat exchange gas into the enclosure, for varying the thermal conductance of said cooling device, by varying the internal pressure of the gas in the enclosure.
  • the cooling device of the invention makes it possible to regulate in temperature the object to be cooled (that is to say to maintain the temperature of this object equal or substantially equal to a desired set temperature) from a cold source at a fixed temperature.
  • the wedges are made of a plastic material.
  • the material is advantageously a thermal insulator. This limits the thermal bridge effect between fins adjacent wedges.
  • the shims have a coefficient of linear thermal expansion greater than that of the fins. Thanks to this, the wedges contract more than the fins during thermal cooling, which avoids a mechanical degradation of the wedges under the action of compression of the fins during temperature changes.
  • each fin comprises a free fixing end of reduced thickness intended to be introduced into a fixing groove in the wedge carried by said fin. Thanks to this, the wedges can be fixed to the fins by simple interlocking or sliding.
  • each wedge comprises three external bearing faces, including two lateral faces and a bottom face, in contact with walls delimiting the interstitial space in which said wedge is inserted and in that each lateral face of support of the wedge is connected to the bearing bottom face of the wedge by an oblique face which is not in contact with said walls. Thanks to this, it limits the heat exchange surface between the wedge carried by a fin and the or neighboring fins.
  • the distance between two adjacent fins, respectively connected to the first heat exchange element and the second heat exchange element is less than or equal to 0.5 mm, advantageously less than or equal to 0.3 mm, advantageously still equal to 0.1 mm.
  • the reduced distance between neighboring fins suppresses natural convection and allows the exchange between the fins 3 and 5 only by gas conduction. This is improved by reducing the distance (inversely proportional). Due to this small gap between the neighboring fins, it is necessary to avoid any deformation of the fins. Indeed, the deformation of a fin It could cause a direct mechanical contact of the latter with a neighboring fin, which would have the effect of considerably impairing the proper functioning of the cooling device.
  • the wedges make it possible to avoid such deformations by mechanically holding the fins in position.
  • the first heat exchange element is thermally connected to heat exchange fins intended to be immersed in the cold source. With these fins, the heat transfer between the cold source and the first heat exchange element is improved.
  • the pump is an adsorption pump containing an adsorbent, a heating module and a thermal connection element to said cold source, intended to evacuate heat.
  • the cold source is also used by the pump to adjust its internal temperature.
  • the cooling device may comprise a saturated cryogenic fluid bath, acting as a cold source, said fluid comprising one of the elements of the group comprising helium, hydrogen, neon, nitrogen, oxygen and argon.
  • the enclosure carries a welding lip to a sealing lip ring.
  • welding lips makes it possible to limit the rise in temperature of the shims during the assembly of the various elements of the cooling device.
  • the length of the wedge carried by a fin is less than the width of said fin.
  • each fin carries at least two shims.
  • the thermal cooling device of the invention has the function of cooling an object, the latter constituting a hot source, from a cold source, for example a bath of cryogenic fluid.
  • the cold source 1 is here a bath of cryogenic fluid. It has a fixed temperature. In the particular embodiment described here, the bath contains saturation liquid helium at a temperature equal to or close to 4.5 K (ie - 269 ° C).
  • the cryogenic fluid could alternatively be hydrogen, neon, nitrogen, oxygen, argon or the like.
  • the heat exchange element 2 with the cold source 1 and the heat exchange element 4 with the object to be cooled 200 are thermal conducting elements. They are made of a material constituting a good thermal conductor, for example copper, and here have a disc shape.
  • the element 2 of heat exchange with the cold source 1 is thermally connected to the cold source 1 here constituted by the cryogenic fluid bath 1.
  • the cryogenic fluid here by immersion of the one of the faces of the thermal conductive disk, called the "submerged face" 20, in the cryogenic fluid bath 1.
  • the submerged face 20 of the conductive element 2 can be extended longitudinally by third heat exchange fins 9 disposed at the bottom interior of the bath 1, as shown in figure 2 . These fins 9 heat exchange with the bath 1 can improve the heat transfer between the bath 1 and the heat exchange element 2.
  • the other side (or side) 21 of the heat exchange element 2, opposite to the immersed face 20, is extended longitudinally by the first heat exchange fins 3. These are confined in the internal chamber of the tube exchanger 6. Thereafter, the term “cold fins” will be called the first fins 3 because they are thermally connected to the cold source 1.
  • the assembly comprising the first heat exchange element 2, the first heat exchange fins 3 and the third heat exchange fins 9 form here a single piece. It is machined from a cylinder full of a good thermal conductor material, here copper. To obtain the fins 3 and 9, grooves are machined in planes parallel to each other and to the longitudinal axis of the cylinder. Each fin 3 or 9 thus extends in a plane parallel to the longitudinal axis and has the shape of a partial longitudinal slice of cylinder.
  • the conductive disc 2 carries ten first fins 3 and five third fins 9.
  • the conductive disc 2 and the cylindrical envelope of the third fins 9 have a diameter which is slightly smaller than the internal diameter of the exchanger tube 6.
  • the first fins 3 have a cylindrical casing of diameter equal to or substantially equal to that of the internal diameter of the exchanger tube 6.
  • the heat exchange element 4 is extended longitudinally by the second fins 5. These are also confined in the internal chamber of the exchanger tube 6. Thereafter, the second fins will be called “hot fins”. because they are thermally connected to the object to be cooled 200.
  • the heat exchange element 4 and the hot fins 5 form here a single piece. This is made from a solid cylinder made of a good thermal conductor material, in this case copper.
  • the hot fins 5 may be formed by machining grooves in the copper cylinder in planes parallel to each other and to the longitudinal axis of the cylinder. Each fin 5 thus extends in a plane parallel to the longitudinal axis and has the shape of a partial longitudinal portion of the cylinder.
  • the conductive disc 4 carries eleven second fins 5.
  • the diameter of the conductive disc 4 is greater than the internal diameter of the exchanger tube 6.
  • the fins 5 have a cylinder-shaped envelope of diameter equal to or substantially equal to that of the internal diameter of the tube exchanger 6.
  • the first and second fins 3 and 5 have a height (in the longitudinal direction) of about 160 mm and a thickness (perpendicular to the plane of the fin) of 2 , 5 mm.
  • the interstitial space, or gap, separating two adjacent fins 3 (or 5) integral with the same heat exchange element 2 (or 4) is here 2.7 mm.
  • the width of a fin (in the direction perpendicular to the longitudinal direction in the plane of the fin) is less than or equal to the diameter of the disc 2 (or the internal diameter of the exchanger tube 6), here equal to 55.5 mm, and varies according to its position: the fins or fins disposed near or on the longitudinal axis of the cylinder are wider than those disposed at the outer periphery.
  • the fins 3 could have other dimensions, including a thickness of between 1 and 10 mm, a height of between 10 and 500 mm and a maximum width of between 10 and 200 mm.
  • the machining of the fins 3, 5 and 9 can be performed by electroerosion.
  • the enclosure 6 is sealed. It comprises a wall here cylindrical which forms a tube of longitudinal axis AX, enclosing a receiving chamber of the first "cold” fins 3 and second "hot” fins 5. Thereafter, this tube will be called “heat exchanger tube” or “exchanger tube” because its internal chamber is the heat exchange seat between the first fins 3 "cold” and the second fins 5 "hot”, interposed between them, as will be explained later.
  • This exchanger tube 6 is for example stainless steel. Stainless steel has several advantages: it can be soldered easily, especially with copper, and has a low thermal conduction, which limits the thermal conduction in the OFF position. The stainless steel heat exchanger tube 6 thus advantageously has a low thermal conductivity.
  • the exchanger tube 6 has a diameter less than or equal to 70 mm, advantageously less than or equal to 65 mm, advantageously still equal to 60 mm and advantageously still greater than or equal to 20 mm.
  • the diameter of the tube depends on the power to be exchanged.
  • the first heat exchange element 2 is disposed at one end of the tube 6. It is here inserted inside the tube 6 and secured thereto by means of a sealing ring 13. welding lip.
  • the second heat exchange element 4 is disposed at the other end of the tube 6, opposite to that receiving the first heat exchange element 2. Its diameter is here greater than the external diameter of the tube 6 and it is abutted against this other end of the tube 6 by means of another sealing ring 16 to welding lip, as will be explained later.
  • the first fins 3, thermally connected to the first element 2 of heat exchange with the cold source 1, and the second fins 5, thermally connected to the second element 4 of heat exchange with the object to be cooled 200, are arranged at the inside the exchanger tube 6, or the enclosure. They are interposed between them and without direct mechanical contact between them.
  • Each cold fin 3 is inserted into an interstitial space separating two adjacent hot fins 5 or a hot fin 5 and the inner face of the exchanger tube 6.
  • each hot fin 5 is inserted into an interstitial space separating two cold fins 3 adjacent or cold fin 3 and the inner face of the exchanger tube 6.
  • the clearance or gap formed between two adjacent fins, respectively cold 3 and hot 5 is 0.1 mm.
  • the gap between each of the two peripheral fins (here hot fins 5), and the inner face of the exchanger tube 6 is of the order of 0.1 mm.
  • each fin 3 (or 5) opposite to that integral with the associated heat exchange element 2 (or 4), carries at least one positioning wedge 8 adapted to position, here center, this fin 3 (or 5) in the interstitial space in which it is inserted.
  • the wedge 8 carried by the fin 3 (or 5) makes it possible to ensure the centering of this fin in the interstitial space in which it is received and to avoid any deformation of the fin, thanks to a forced holding in the center interstitial space.
  • the shims 8 are made of another thermally insulating material, having a low thermal conductivity, advantageously less than or equal to 0.2 Wm -1 .K -1 or less than 0.3 Wm -1 .K -1 .
  • they are about plastic, in particular polyimide plastic. They are preferably not metal or metal alloy.
  • the constituent material of the shims 8 advantageously has a coefficient of linear thermal expansion greater than that of the material constituting the fins 3, 5 (in this case copper). As a result, the thermal contraction of the wedges 8 is greater than that of the fins 3, 5, which makes it possible to prevent damage to the wedges by the fins when they contract under the effect of cooling.
  • FIG 5 schematically shows a wedge 8, according to a particular embodiment, in cross section.
  • the shim 8 intended to be carried by a fin 3 (or 5) comprises three outer bearing faces 80-82: two lateral faces 80, 81 and a bottom face 82.
  • the shim 8 carried by a fin 3 (or 5) is inserted in an interstitial space between two fins 3, 5 or between a fin 5 and the wall of the exchanger tube 6, the two lateral faces 80, 81 of the shim 8 are in contact with the lateral walls delimiting the interstitial space and the bottom surface 82 is in contact with the heat exchange element 4 (or 2) forming the bottom of the interstitial space.
  • Each lateral bearing face 80, 81 of the wedge 8 is connected to the bearing base face 82 by an oblique face 83, 84 which is not in contact with the walls delimiting the interstitial space. Thanks to this, the heat exchange surface is reduced between the shim 8 and the neighboring elements (fin 3 or 5, heat exchange element 2 or 4 or exchanger tube 6), which contributes to limiting the effect of " thermal bridge "(that is to say thermal transfer) wedges 8.
  • the thickness of the bottom of the shim is chosen so as to ensure a desired spacing of the fins 3 (or 5) relative to the element d heat exchange 4 (or 2) to limit the heat exchange between these fins 3 (or 5) and the heat exchange element 4 (or 2) and thus further reduce the effect of "thermal bridge" shims 8.
  • This bottom thickness is advantageously between 1 and 10 mm.
  • each wedge is in permanent contact (without play) with the side walls of the interstitial space in which it is located. More preferably, each shim is also in permanent contact (without play) with the fin on which it is mounted or fixed. These different contacts can be more or less prestressed. Thus, the fin can not move laterally except to compress the material forming the wedge.
  • each wedge is in permanent contact (without play) with the bottom of the interstitial space in which it is located. More preferably, each shim is also in permanent contact (without play) with the end face of the fin on which it is mounted or fixed. Thus, the fin can not move axially towards the bottom of the interstitial space except compressing the material forming the wedge.
  • Each wedge thus makes it possible to immobilize a fin at least laterally, that is to say perpendicularly to the main faces of the fin or horizontally in the planes of the fins.
  • FIGS 2 , 4A and 4B Each wedge can also make it possible to immobilize a fin at least axially, that is to say parallel to the main faces of the fin or vertically in the planes of the fins. figures 2 , 4A and 4B .
  • the mounting situation in contact or prestressed between the shims and the fins is found at room temperature, for example at 20 ° C. Indeed, during cooling, the differential contraction between the materials of the wedges and fins contributes to reducing the contacts between the wedges and the fins, or even ideally to remove them.
  • Each fin 3 (or 5) may carry at its free end, opposite to that integral with the associated heat exchange element 2 (or 4), one or more positioning wedges, or centering, 8.
  • the length of the shim 8 that is to say its dimension according to the direction perpendicular to the axis AX in the plane of the fin, is equal to the width of the fin or less than it.
  • the different shims carried by a fin are spaced from each other and preferably distributed uniformly along the fin so as to ensure a good mechanical support of the fin.
  • each fin 3, 5 carries two shims.
  • Fixing wedges 8 to the fins 3 (or 5) can be made by interlocking a projecting part of one of the two elements (wedge or fin) in a recessed portion formed in the other element (fin or wedge) .
  • each fin 3 (or 5) comprises a fixing free end, of reduced thickness, intended to be introduced into an attachment groove 85 formed in the shim 8.
  • the groove 85 has a shape complementary to that of the fixing end of the fin and here has a U-shaped cross section.
  • the depth of the groove 85 is advantageously between 1 and 10 mm.
  • the width of the groove 85 is advantageously between 1 and 10 mm.
  • the wedges 8 have a symmetry with respect to a median plane which extends here in the middle of the groove 85 perpendicular to the plane of the figure 5 . In addition, they have a width, orthogonal to this plane of symmetry, which is equal to the width of the interstitial space between two adjacent fins 3 and 5 (here 2.7 mm). This symmetry makes it possible to ensure the centering of the fin in the interstitial space in which it is inserted.
  • a shim generally has a parallelepipedal shape of which two parallel edges are chamfered (between the faces 81 and 82 and between the faces 80 and 82). The chamfers form the oblique faces 83 and 84.
  • the parallelepipedal shape also has the groove 85 or groove 85. This groove is intended to be fixed, for example by interlocking on one end of a fin, in particular to be fixed by example by interlocking on a tongue 86 formed at one end of a fin.
  • the shims are used to relatively position the fins and avoid their contacts which could be related to a release of the constraints in the fins and thus to the deformation of the fins (following their machining).
  • the exchanger tube 6 is closed by the first heat exchange element 2, at one of its ends, and by the second heat exchange element 4, at its other end. It contains a confined internal heat exchange chamber which contains the first fins 3 and the second fins 5. This heat exchange chamber is sealed, as will be explained later. It contains a heat exchange gas 7 at a desired internal pressure.
  • This heat exchange gas is one of those previously mentioned for the bath 1 of cryogenic fluid (hydrogen, neon, nitrogen, oxygen, argon or other). Generally, the heat exchange gas used is the same as that of the bath 1 constituting the cold source.
  • the assembly comprising the tube (or enclosure) 6, the heat exchange elements 2 and 4, the first and second heat exchange fins 3, 5 and the heat exchange gas 7 allows a transfer of heat between the source 1 and the object to be cooled 200.
  • This device has a certain thermal conductance which depends in particular on the internal pressure of the gas 7 in the chamber 6. By varying this pressure, the thermal conductance of the device can be varied. 'invention.
  • the cooling device 100 comprises an element for adjusting the heat exchange gas pressure in the enclosure, for example here a pump 10 for introducing and extracting heat exchange gas 7 in the internal chamber of the chamber 6.
  • the pressure variation of the heat exchange gas in the chamber makes it possible to obtain a variation of the thermal conductance and thus makes it possible to regulate the temperature of the second heat exchange element 4 that is to say to maintain this temperature equal to or substantially equal to a desired value, regardless of the temperature variations of the object to be cooled, from the cold source (here bath 1) at a fixed temperature .
  • the pump 10 here uses the cryogenic fluid bath 1 as a cold source. It is connected to the bath 1 by a calibrated braid acting as thermal resistance.
  • the control module controls the operation of the thermal resistance to adjust the internal temperature of the pump 10 and therefore the temperature of the adsorbent.
  • the adsorbent here comprises grains of activated carbon, for example carbonized coconut (activated carbon), housed in an internal chamber of the pump 10.
  • gas atoms 7 stick to the surface of the grains of carbon. coal forming layers.
  • the number of layers of exchange gas atoms bonded to the grains of coal depends on the temperature of the grains, in other words on the internal temperature of the pump 10. By varying this internal temperature, using the heating module, the control module can modulate the amount of gas trapped by the pump 10 and thus vary the internal pressure of the gas 7 in the chamber 6.
  • the inner chamber of the tube 6 is connected to a filling tube or capillary 12A, via a barrel 12B. Initially, heat exchange gas 7 is introduced into the chamber from an external gas supply (not shown) by the filling capillary.
  • the internal chamber of the tube 6 is also connected to a capillary or tube 11 for connection to the pump 10.
  • the pump 10 is thus mounted on the exchanger tube 6, advantageously close to the adjacent end of the cryogenic bath 1. Two openings of receiving the capillary 11 and the barrel 12B are formed in the wall of the tube 6.
  • the heat exchange gas pressure adjusting element in the chamber enables the thermal conductance of the thermal cooling device to be adjusted and controlled actively and at will.
  • the thermal conductance of the thermal cooling device can be set to a given value independently of other physical parameters, in particular regardless of the temperature of the cold source and / or the temperature of the object to be cooled.
  • the first heat exchange element 2 is assembled to the exchanger tube 6 via the ring 13.
  • the ring 13 is a flap or lip ring.
  • the end of the ring 13 carrying the flap (or the lip) is introduced into the end portion of the tube 6 and mounted around the heat exchange disk 2.
  • the ring 13 is here fixed to the exchange element 2 by soldering and the tube 6 by TIG welding at the lip (or flap).
  • the ring 13 protrudes out of the tube 6. It is secured, at its other end (opposite to that carrying the flap or the lip), to another ring 14 for adaptation to a reservoir containing the bath 1 of cryogenic fluid (no represented on the Figures 3A and 3B ), here by TIG welding.
  • the adaptation ring 14 is secured here by TIG welding, to a flange 15 for connection to the tank of the bath 1.
  • This connecting flange 15 is intended to be fixed, by means of a seal, to the tank, to the right to an adapted opening formed therein.
  • the lip ring 13, the adapter ring 14 and the connecting flange 15 are here made of stainless steel.
  • the tube 6 is connected to the second heat exchange element 4 by means of the other other lip seal ring 16.
  • the ring 16 is mounted around a solid cylinder portion connecting the second fins 5 and the element 4 of heat exchange. It has, at one of its ends, a lip in the form of a flange which is secured to another lip-shaped flange provided at the end of the exchanger tube 6, here by TIG welding. The other end of the ring 16 is joined by brazing to the heat exchange element 4.
  • the heat exchange element 4 is here secured, for example by screwing, to the object to be cooled, as shown in FIG. figure 3B .
  • the assembly can also be made by direct contact, by welding or, for the sake of ease of assembly, with the aid of an intermediate piece (for example copper).
  • welding lips makes it possible to greatly limit the rise in temperature of the device and thus to protect the plastic wedges against damage due to high temperatures. They also facilitate the subsequent disassembly of the cooling device, in particular to perform a re-centering of the fins in case of problems.
  • the bath 1 contains, for example, saturation liquid helium at a fixed temperature equal to approximately 4.5 K.
  • the heat exchange fins 9 are immersed in the bath 1 and the face of the heat exchange disk 2 carrying these fins 9 is in direct contact with the cryogenic fluid.
  • the internal chamber of the exchanger tube 6 is filled with heat exchange gas 7 at an internal pressure controlled by the pump 10.
  • the thermal conductance of the cooling device 100 can be modulated in time as a function of the heat transfer requirements between the bath 1 and the object to be cooled 200.
  • a temperature sensor measures the temperature of the object to be cooled 200. Measured temperature values of the object 200 are regularly transmitted to the control module of the pump 10, which consequently adjusts the internal pressure of the gas 7 (if necessary changing it over time) to obtain a stable target temperature or
  • the cooling device 100 thus makes it possible to cool the object 200 to a desired setpoint temperature and to regulate this temperature over time, otherwise to keep the object 200 at a stable temperature. equal to or substantially equal to this set temperature, by varying the internal pressure of the exchange gas 7.
  • the cooling device of the invention makes it possible to control the heat transfer at cryogenic temperatures between a cold source (here a bath of cryogenic fluid) and an object to be cooled and to regulate in temperature this object, in an easy, flexible and economic. It allows a thermal regulation over a wide range of temperatures, from the same cold source and by means of internal gas pressure adjustments, simple to perform.
  • the device of the invention has a structure similar to that of the device described in the document US 2005/0230097 but is adapted to allow heat transfer at much higher power levels. This adaptation is made possible thanks to the use of wedges 8 of positioning, or centering.
  • the cutoff ratio of the cooling device 100 is for example between 40 and 100, while it is generally greater than 1000 for conventional thermal switches.
  • a cooling device according to the invention having a cut-off ratio of 40 would make it possible to regulate in temperature between 5.4 K and 40 K an experiment consuming 2 W of power from a bath of saturation helium having a temperature of 4.4 K, without varying the helium consumption which would be substantially 0.1 g / s.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
EP17160161.0A 2016-03-10 2017-03-09 Vorrichtung zur thermischen kühlung eines objekts mithilfe einer kühlquelle, wie etwa einem kühlmittelbad Withdrawn EP3217137A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1651987A FR3048770B1 (fr) 2016-03-10 2016-03-10 Dispositif de refroidissement thermique d'un objet a partir d'une source froide telle qu'un bain de fluide cryogenique

Publications (1)

Publication Number Publication Date
EP3217137A1 true EP3217137A1 (de) 2017-09-13

Family

ID=56087334

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17160161.0A Withdrawn EP3217137A1 (de) 2016-03-10 2017-03-09 Vorrichtung zur thermischen kühlung eines objekts mithilfe einer kühlquelle, wie etwa einem kühlmittelbad

Country Status (2)

Country Link
EP (1) EP3217137A1 (de)
FR (1) FR3048770B1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110108060A (zh) * 2019-05-20 2019-08-09 中国科学院理化技术研究所 一种吸附泵及气隙式热开关
EP3993587A1 (de) * 2020-11-02 2022-05-04 Sungrow Power Supply Co., Ltd. Wärmeableitende vorrichtung eines wasserkühlers und elektrische vorrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0325270A (ja) * 1989-06-23 1991-02-04 Toshiba Corp 熱スイッチ
US5842348A (en) * 1994-10-28 1998-12-01 Kabushiki Kaisha Toshiba Self-contained cooling apparatus for achieving cyrogenic temperatures
US20050230097A1 (en) 2001-07-10 2005-10-20 Shirron Peter J Passive gas-gap heat switch for adiabatic demagnitization refrigerator
WO2007147981A1 (fr) 2006-06-23 2007-12-27 Commissariat A L'energie Atomique Interrupteur thermique a gaz a element d'echange thermique mobile

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0325270A (ja) * 1989-06-23 1991-02-04 Toshiba Corp 熱スイッチ
US5842348A (en) * 1994-10-28 1998-12-01 Kabushiki Kaisha Toshiba Self-contained cooling apparatus for achieving cyrogenic temperatures
US20050230097A1 (en) 2001-07-10 2005-10-20 Shirron Peter J Passive gas-gap heat switch for adiabatic demagnitization refrigerator
WO2007147981A1 (fr) 2006-06-23 2007-12-27 Commissariat A L'energie Atomique Interrupteur thermique a gaz a element d'echange thermique mobile

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110108060A (zh) * 2019-05-20 2019-08-09 中国科学院理化技术研究所 一种吸附泵及气隙式热开关
EP3993587A1 (de) * 2020-11-02 2022-05-04 Sungrow Power Supply Co., Ltd. Wärmeableitende vorrichtung eines wasserkühlers und elektrische vorrichtung

Also Published As

Publication number Publication date
FR3048770B1 (fr) 2018-03-23
FR3048770A1 (fr) 2017-09-15

Similar Documents

Publication Publication Date Title
EP2824777B1 (de) Laserkristall, der ein Kühlsystem für den Kristall mit einer Flüssigkeit umfasst
FR2527838A1 (fr) Dispositif et procede de transfert thermique entre solides, avec assistance par un gaz, pour une tranche de semi-conducteur
FR2925254A1 (fr) Dispositif de refroidissement d'une carte electronique par conduction a l'aide de caloducs,et procede de fabrication correspondant.
FR2702831A1 (fr) Procédé et dispositif de refroidissement de l'enceinte d'un échangeur thermique.
EP3217137A1 (de) Vorrichtung zur thermischen kühlung eines objekts mithilfe einer kühlquelle, wie etwa einem kühlmittelbad
CA2523371C (fr) Systeme de compensation en temperature reglable pour resonateur micro-ondes
EP3891835B1 (de) Brennstoffzelle beinhaltend wenigstens ein integriertes zugelement
FR2937795A1 (fr) Dispositif electronique a matrice de diodes electroluminescentes de forte puissance comprenant des moyens de refroidissement ameliores
EP3520166A1 (de) Temperaturregelungsvorrichtung
WO2017216450A1 (fr) Chambre de combustion de moteur fusee avec ailettes a composition variable
EP2327127B1 (de) Optische pumpstruktur
FR3055242A1 (fr) Outil de pressage a chaud, son procede de mise en oeuvre, installation et procede de fabrication correspondants
FR2813662A1 (fr) Evaporateur capillaire pour boucle de transfert
WO1993013556A1 (fr) Systeme de refroidissement pour module 'multi-puces'
BE1012408A3 (fr) Oscillateur de laser a gaz.
EP4323711B1 (de) Zweiphasige wärmeübertragungsvorrichtung mit flüssigkeitsüberlauftank
FR2864862A1 (fr) Dispositif de refroidissement pour pile a combustible et pile a combustible utilisant un tel dispositif
EP3731613B1 (de) Verfahren zur integration eines wärmeübertragungsrohrs in eine platte, die einen elektrischen kontakt bilden soll
FR3056829A1 (fr) Dispositif de regulation thermique de batterie
EP3743928B1 (de) Lagerkorb für radioaktive materialien mit optimiertem platzbedarf und mit gehäusen mit genauerer geometrie
EP3246648B1 (de) Kühlvorrichtung mit pulsierendem wärmeleitrohr
FR3128281A1 (fr) Caloduc de type à pompage capillaire avec rainures réentrantes à gestion de liquide améliorée.
WO2024104573A1 (fr) Structure diphasique à sens unique de transfert thermique
FR3094842A1 (fr) Corps de régulation thermique d’un dispositif de stockage d’énergie de véhicule automobile électrique ou hybride
WO2014111445A1 (fr) Emballage pour le transport et/ou l'entreposage de matieres radioactives comprenant une protection anti-feu amelioree

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20180313

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20201001