EP2066991B1 - Installation frigorifique comportant un élément de raccordement chaud et un élément de raccordement froid, ainsi qu'un tube échangeur de chaleur relié à ces éléments de raccordement - Google Patents

Installation frigorifique comportant un élément de raccordement chaud et un élément de raccordement froid, ainsi qu'un tube échangeur de chaleur relié à ces éléments de raccordement Download PDF

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Publication number
EP2066991B1
EP2066991B1 EP07803233.1A EP07803233A EP2066991B1 EP 2066991 B1 EP2066991 B1 EP 2066991B1 EP 07803233 A EP07803233 A EP 07803233A EP 2066991 B1 EP2066991 B1 EP 2066991B1
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EP
European Patent Office
Prior art keywords
heat pipe
parts
connection element
pipeline
area
Prior art date
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Not-in-force
Application number
EP07803233.1A
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German (de)
English (en)
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EP2066991A1 (fr
Inventor
Marijn Pieter Oomen
Peter Van Hasselt
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Siemens AG
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Siemens AG
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Publication of EP2066991A1 publication Critical patent/EP2066991A1/fr
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Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/006—Thermal coupling structure or interface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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
    • 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
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • 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
    • F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
    • 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
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F6/00—Superconducting magnets; Superconducting coils
    • H01F6/04—Cooling

Definitions

  • a refrigeration system with the above features for example, from the DE 36 21 562 A1 out.
  • Cooling systems eg cooling systems for superconducting magnets
  • a liquid refrigerant eg helium
  • a temperature of typically 4.2 K can be used.
  • large quantities of the corresponding refrigerant are necessary.
  • the superconducting magnet there is also the possibility that it loses its superconducting properties, for example by exceeding a critical current for the corresponding superconducting material or a critical magnetic field. In such a case, the superconducting material quickly generates a large amount of heat. The resulting heat leads in a bath cooling to a boiling of the refrigerant within the cryostat. Large amounts of gaseous refrigerant leads to a rapid increase in pressure within the cryostat.
  • cooling systems are designed without a refrigerant bath.
  • Such cooling systems can do without any refrigerant.
  • the cooling capacity is introduced in this case only by solid-state heat conduction in the areas to be cooled.
  • the areas to be cooled may be replaced by a so-called solid state cryobus of e.g. Copper connected to a chiller.
  • Another possibility is to connect the areas to be cooled and the chiller to a closed piping system in which a small amount of refrigerant circulates.
  • the advantage of such cooling systems without a refrigerant bath continues to be that they are easier to adapt to moving loads to be cooled as cooling systems, which have a refrigerant bath.
  • Cooling systems without a refrigerant bath are therefore particularly suitable for superconducting magnets of a so-called gantry, as used in ion beam therapy for combating cancer.
  • the cooling capacity can be provided in the cooling systems described above typically a chiller with a cold head in particular a Stirling cooler available.
  • a superconducting magnet in which a cold head with its second stage is directly mechanically and thermally connected to the support structure of a superconducting magnet winding, goes, for example, from US 5,396,206 out.
  • the necessary cooling capacity is introduced directly into the superconducting magnet windings in the aforementioned superconducting magnet by solid-state heat conduction. If, however, a cold head has to be replaced, for example, for maintenance purposes, the abovementioned cooling device for a superconducting magnet has a decisive technical problem.
  • During the exchange process may freeze air or other gases on the cryogenic contact surface, in this case the superconductive winding support structure. Ice formed at these points leads to a poor thermal connection of the subsequently re-used cold head with the support structure of the winding.
  • the freezing of ambient gases at the cryogenic contact surfaces can be avoided by purposely flooding the space around these contact surfaces with gas.
  • this is expensive and leads to a large consumption of purge gas or vaporized refrigerant for this purpose.
  • EP 0 696 380 B1 discloses a superconducting magnet with a cryogen-free refrigeration system.
  • the disclosed refrigeration system has a thermal bus of good thermal conductivity material such as copper, which is connected to the superconducting magnet.
  • the thermal bus can still be connected to two cold heads.
  • the two cold heads are arranged symmetrically to the thermal bus. They can each be approached from opposite sides to the thermal bus. In this way one or both cold heads can be brought into thermal contact with the thermal bus.
  • the cooling capacity is introduced in accordance with one or both cold heads in the thermal bus.
  • DE 102 11 568 B4 discloses a refrigeration system with two cold heads, which are connected via a piping system in which a refrigerant is circulatory according to a thermosiphon effect, connected to the parts to be cooled of a device.
  • the piping system has a branch. At the ends of the branches there is a respective refrigerant space, which is connected to a cold head. Liquid refrigerant decreases, starting from one of these refrigerant chambers, gravity driven to the parts of the device to be cooled, at which the heat transfer takes place. Gaseous refrigerant in the piping system in turn rises to the two cold heads, where it is reliquefied.
  • Such a cycle of the refrigerant may take place in the piping system both in the case where only one cold head is operating and in the case where both cold heads are operating.
  • the refrigeration system is dimensioned in such a way that a single cold head applies the cooling capacity necessary for the parts of the device to be cooled, another cold head can be exchanged during operation of the refrigeration system.
  • the piping system between the branch and the refrigerant spaces, which are each connected to a cold head made of poor thermal conductivity material. In this way, the losses can be limited by solid-state heat conduction.
  • gaseous refrigerant is always added to the Climb to the point where there is no or a disconnected cold head. Thus, although the losses can be limited by solid-state heat conduction, but not the losses caused by circulating refrigerant.
  • the refrigerating machine comprises a vacuum housing accommodating the vessel, a radiation shield arranged between the vessel and the housing, a cooling apparatus for cooling at least one shield and the vessel and a heat-conducting coupling arranged between the cooling apparatus and at least one shield and the vessel Production and interruption of heat transfer between these parts.
  • a cryogenic cooling device for cooling an object in a vacuum container.
  • the cooling device comprises a hot and a cold section, which are separated by a cold cylinder.
  • a heat transfer device is arranged in each case. A heat exchange between the heat transfer means via a substance, as long as it is present in gaseous form.
  • Object of the present invention is to provide a refrigeration system in which the parts to be cooled means of a device with a heat pipe in which a liquid is circulated by a thermosiphon effect, are connected to a heat sink, wherein the parts to be cooled of a device without a Mechanical separation should be largely thermally decoupled from the heat sink.
  • This object is achieved with the measures specified in claim 1.
  • the present invention is based on the following considerations: The heat exchange between the heat sink and the parts of a device to be cooled takes place essentially by the liquid which can be circulated in the heat pipe according to a thermosiphon effect. For thermal separation of the heat sink from the parts to be cooled of the device, the heat pipe can be pumped off via a pipe connected to its interior.
  • the heat pipe should be made of a poor thermal conductivity material at the same time. By these measures, the thermal connection between the heat sink and the parts to be cooled of the device is reduced to a defined by the solid state heat conductivity of the heat pipe low level.
  • the refrigeration system should contain at least one hot connection element, which is thermally connected to parts of a device to be cooled, and a cold connection element, which is thermally connected to a heat sink containing.
  • a heat pipe made of poorly heat-conducting material should be connected at a first end to the hot connection element and at a second end to be mechanically detachable with the cold connection element.
  • the interior of the heat pipe should be at least partially filled with a liquid which can be circulated according to a thermosiphon effect.
  • the refrigeration system should include a pipeline having a first end to the interior is connected to the heat pipe and is configured such that at least parts of the pipeline are geodetically higher than the liquid level.
  • the liquid should be able to be pumped out of the heat pipe via the pipeline.
  • the refrigeration system according to the invention should be rotatable about an axis which runs substantially parallel to an axis of symmetry of the heat pipe.
  • the heat pipe should continue to have a larger cross-section in a first region which is connected to the warm connection element than in a second region which is connected to the cold connection element.
  • the parts of the heat pipe which connect the first and the second region to one another should be designed such that in the second region condensed refrigerant can pass unimpeded under the influence of gravity to the first region.
  • a refrigeration system with the aforementioned features should be particularly advantageous for movable, in this case rotatably arranged to be cooled parts of a device used.
  • the thermal contact when reinserting the heat sink will turn out much better than in the case in which there is significant ice formation at the contact surfaces. Furthermore, the cryogenic region in which the parts of the device to be cooled, due to the thermal decoupling, is prevented from penetrating into this region heat flows. In this way, even when replacing the heat sink to be cooled parts of a device at the desired low temperature.
  • the thermal contact between the chiller and the parts to be cooled of the device is ensured at any time with a rotation of the parts to be cooled of a device.
  • a refrigeration system can be specified, which allows even with a single heat sink use, without heating the parts to be cooled is necessary to exchange the heat sink or wait or remove temporarily.
  • the refrigeration system according to the invention is particularly suitable for devices in the field of superconducting technology.
  • FIG. 1 shows the schematic structure of a refrigeration system 100.
  • a cryostat 108 are the parts to be cooled 102 of a device.
  • the device parts to be cooled 102 may be, for example, the magnet windings of a superconducting magnet or other parts of the superconducting technique.
  • a heat shield 112 is mounted to enhance thermal isolation.
  • the cooling capacity for the parts to be cooled 102 of the device is provided by a refrigerator 109, such as a cold head or a Stirling cooler.
  • a cold head can be used, which operates on the Gifford-McMahon principle.
  • Such Two-stage chiller can according to the present embodiment with its first stage 111 thermally connected to the heat shield 112.
  • the connection between the first stage 111 of the refrigerator 109 and the heat shield 112 may preferably be a releasable mechanical connection, such as a screw or clamp connection, which simultaneously ensures good thermal contact of the components.
  • the second stage 110 of the refrigeration machine 109 represents the actual heat sink 104 of the refrigeration system 100.
  • the second stage 110 of the refrigerator 109 is thermally connected to a cold connection element 103.
  • the corresponding connection may preferably be a screw connection. That is, the refrigerator 109 is detachably screwed with its second stage 110 in the cold connection element 103. Any other mechanical connection which is releasable and at the same time ensures good thermal contact between the second stage 110 of the refrigerator 109 and the cold connection element 103 is also for the in FIG. 1 illustrated embodiment suitable.
  • the connecting elements 101 and 103 may be part of the parts 102 to be cooled of a device or the heat sink 104. They can continue to be integrated into the corresponding components or permanently connected to them.
  • the chiller 109 is partially located in a separately evacuable maintenance room 113. This maintenance room 113 is separated from the rest of the evacuatable space of the cryostat 108.
  • the cold connection element 103 is connected to a heat pipe 105 with good thermal conductivity and preferably also mechanically.
  • the heat pipe 105 is connected to a warm connection element 101. This compound is also designed to conduct heat well and may preferably also be a mechanical connection.
  • the warm connection element 101 is in turn connected to a good heat-conducting with the parts to be cooled 102 of a device.
  • a liquid 106 which can circulate in the heat pipe 105 in accordance with a thermosiphon effect.
  • the heat pipe 105 itself, however, consists of a poorly heat-conducting material.
  • the heat pipe 105 If the heat pipe 105 is completely filled with the liquid, it can assume a lower density in the upper cold region of the heat pipe 105 than in the lower, warmer region of the heat pipe 105. Due to the density differences of the liquid 106, a circulation can occur in the heat pipe 105 adjust according to the so-called. Thermosiphon effect, which causes a heat transfer from the parts to be cooled 102 of the device to the heat sink 104.
  • the heat pipe 105 may be only partially filled with a liquid 106.
  • a circulation of the liquid 106 can be set in two different phases, for example liquid-gaseous. Accordingly, gaseous liquid is liquefied in the portion of the heat pipe 105 which is in thermal contact with the cold joint 103. Condensed liquid 106 moves gravity driven into the in FIG. 1 shown below portion of the heat pipe 105, which is in thermal contact with the hot connector 101. In this part of the heat pipe 105, the liquid 106 delivers the cooling capacity to the hot connector 101 (and thus also to the parts of the device 102 to be cooled), whereupon gaseous liquid 106 rises again into the upper part of the heat pipe.
  • the cold connector 103 acts as a condenser and the hot connector acts as an evaporator. In this way, a good thermal connection between the refrigerator 109 and its second stage 110 and the parts to be cooled 102 of a device can be ensured.
  • the necessity may arise that a refrigeration machine 109 must be replaced, for example, for maintenance work or due to a defect.
  • the liquid 106 which is located within the heat pipe 105, is pumped out via a pipe 107 leading to the outside. It is sufficient in many cases, the liquid 106 for the most part pump out of the heat pipe 105; but it can also be completely removed from the heat pipe 105. By removing the liquid 106 from the heat pipe 105, the thermal conductivity of the heat pipe 105 is significantly reduced.
  • a heat conduction takes place in the following only as a result of solid-state heat conduction via the material of the heat pipe 105.
  • the heat pipe 105 made of a poor thermal conductivity material such as stainless steel, the thermal conduction between the connecting elements 101, 103 can be reduced to a minimum.
  • materials for the heat pipe 105 in addition to stainless steel and various plastics, ceramics or other low temperature suitable materials can be used.
  • Another measure for minimizing the heat conduction is to make the heat pipe 105 particularly thin-walled and / or with small geometrical dimensions.
  • the maintenance room 113 can be ventilated. Due to the ambient air flowing into the maintenance space 113, the cold connection element 103 and the previously cold parts of the chiller 109 begin to heat up.
  • the maintenance room 113 can also be flooded with a special purge gas, such as dried air, nitrogen or helium.
  • the refrigerator 109 can be removed from the refrigeration system 100.
  • the previously deep-cold connection element 103 is thermally decoupled from the remaining still very cold parts, in particular the warm connection element 101 and the parts 102 to be cooled of a device and will therefore heat up quickly to a temperature close to room temperature.
  • Superconducting magnet windings are particularly suitable for irradiation systems, as used in particle therapy, e.g. to fight cancer.
  • Such superconducting magnet windings are preferably mounted in a so-called gantry, which is rotatable about a fixed axis.
  • FIG. 2 shows an embodiment of the generally designated 100 refrigeration system, wherein the entire refrigeration system 100, including the parts to be cooled 102 are arranged rotatably about an axis A.
  • the refrigeration system 100 are the parts to be cooled 102 in a cryostat 108, which additionally has a heat shield 112.
  • the refrigerator 109 is preferably designed rotationally symmetrical with respect to a further axis B.
  • the refrigerator 109 is housed in a maintenance room 113, which is evacuated separately from the cryostat 108.
  • the first stage 111 of the refrigerator 109 is connected to the heat shield 112, the second stage 104 of the refrigerator 109 is connected to the cold connector 103.
  • the heat pipe 105 is located with a first part 202 in thermal, preferably also mechanical connection with the cold connection element 103. Another part 201 of the heat pipe 105 is in thermal, preferably also mechanical contact with the warm connection element 101 Heat pipe 105 has a smaller cross section than the second part 201 of the heat pipe 105.
  • the part 203 of the heat pipe 105 which connects the first part 202 and the second part 201 of the heat pipe 105, is configured in such a way that condensed liquid 106 can pass unhindered from the first region 202 into the second region 201 due to gravity ,
  • the entire heat pipe 105 may preferably have the shape of a truncated cone closed on both sides. Such a heat pipe 105 may further be connected to the refrigerator 109 so that the axis of symmetry of the truncated cone coincides with the axis B.
  • a pipe 107 is connected to the heat pipe 105.
  • the pipeline 107 has such a shape that any liquid 106 entering the pipeline 107 from the heat pipe 105 can not pass unhindered to the outer part of the pipeline 107 that is in communication with the cryostat 108.
  • the pipeline 107 has a part 204 bent in the direction of the axis A.
  • the liquid 106 can be pumped out of the heat pipe 105 through the pipe 107. In this way, a thermal separation between the parts to be cooled 102 of a device and the heat sink 104 is achieved.
  • the working space 113 is aerated after the liquid 106 has been pumped off.
  • the parts of the working space 113 which are arranged between the mounting flange of the first stage 111 of the refrigerator with the heat shield 112 and the condenser 103, can be designed to be flexible.
  • a flexible configuration can be done for example by means of a bellows.
  • the condenser 103 can be moved along the axis B due to a flexible configuration of the heat pipe 105 be.
  • the heat pipe 105 may also have a bellows for this purpose.
  • FIG. 3 shows a further embodiment of a generally designated 100 refrigeration system.
  • refrigeration system 100 is opposite to those in FIG. 2 shown is extended to an additional cooling system.
  • a refrigerant space 301 is in thermal, preferably also in mechanical contact with the cold connection element 103.
  • This refrigerant space 301 can be filled by a feed line 302 from a geodetically higher location.
  • a same or similar refrigerant can be used as it is used for the heat pipe 105. Usable are, for example, helium, neon or nitrogen.
  • a piping system 303 is connected, which is connected over a large area with the parts to be cooled 102 of a device.
  • evaporating refrigerant can escape via an exhaust pipe 304 from the piping system 303. In this way, an overpressure in the piping system 303 is avoided.
  • the auxiliary cooling device may e.g. be used so that the parts to be cooled 102 of a device first with nitrogen, which is inexpensive and readily available, are pre-cooled before using the chiller 109, the parts to be cooled 102 are cooled to even lower temperatures.
  • the additional cooling device it is technically necessary to stop the refrigeration system 100 in its possible rotation about the axis A or at least to move it so slowly that in the pipeline system 303, a gravity-driven refrigerant circuit, which is based on a thermosiphon effect, can set ,

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  • Engineering & Computer Science (AREA)
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Claims (14)

  1. Installation (100) frigorifique comprenant au moins
    a. un élément (101) de liaison chaud, qui est relié thermiquement à des parties (102) à refroidir d'un dispositif,
    b. un élément (103) de liaison froid, qui est relié thermiquement à un puits (104) de chaleur,
    c. un caloduc (105) en matériau mauvais conducteur de la chaleur, qui, à une première extrémité à l'élément (101) de liaison chaud et à une deuxième extrémité, est relié, de manière amovible mécaniquement, à l'élément (103) de liaison froid et dont l'intérieur est empli, au moins en partie, d'un liquide (106) pouvant circuler suivant un effet de thermosiphon et
    d. une canalisation (107), qui communique à une première extrémité avec l'intérieur du caloduc (105) et qui est conformée de manière à ce qu'au moins des parties de la canalisation (107) soient géodésiquement plus hautes que le niveau du liquide,
    e. dans lequel, pour une séparation thermique des éléments (101, 103) de liaison, le liquide (106) peut être pompé par la canalisation (107),
    caractérisée en ce que
    f. il est prévu une possibilité de tourner autour d'un axe (A), qui est sensiblement parallèle à un axe (B) de symétrie du caloduc (105) et
    g. le caloduc (105 a, dans une première région (201), qui est reliée à l'élément (101) de liaison chaud, une section transversale plus grande que dans une deuxième région (202), qui est reliée à l'élément (103) de liaison froid et les parties (203) du caloduc, qui relient la première (201) et la deuxième régions (202) entre elles, sont conformées de manière à ce que du fluide (106) réfrigérant, condensé dans la deuxième région (202), puisse, sous l'influence de la force de la gravité, arriver sans obstacle dans la première région (201).
  2. Installation (100) frigorifique suivant la revendication 1, caractérisée en ce que les parties à refroidir du dispositif (102) sont disposées dans un cryostat (108) pouvant être mis sous vide et en ce que la deuxième extrémité de la canalisation (107) est en dehors du cryostat (108).
  3. Installation (100) frigorifique suivant la revendication 2, caractérisée en ce qu'il y a une machine (109) frigorifique à plusieurs étage, ayant un premier étage (111) et un deuxième étage (110), le puits (104) de chaleur étant constitué par le deuxième étage (110) et le premier étage (111) est relié, d'une manière amovible mécaniquement, à un bouclier (112) thermique disposé à l'intérieur du cryostat (108).
  4. Installation (100) frigorifique suivant la revendication 3, caractérisée en ce qu'au moins des parties de la machine (109) frigorifique sont mises, de manière remplaçable, dans un espace (113) d'entretien, séparé du cryostat (108) pouvant être mis sous vide et pouvant être mis sous vide.
  5. Installation (100) frigorifique suivant l'une des revendications précédentes, caractérisée en ce que le liquide (106) se présente sous la forme d'un mélange à deux phases.
  6. Installation frigorifique suivant l'une des revendications précédentes, caractérisée en ce que la canalisation (107) est reliée, à ses extrémités proches de l'axe (B) de symétrie du caloduc (105), au caloduc (105) et au côté extérieur du cryostat (108) et la canalisation (107) a, dans la direction dans laquelle elle s'étend, au moins une région (204) intermédiaire proche de l'axe (A).
  7. Installation frigorifique suivant la revendication 6, caractérisée en ce que la région (204) intermédiaire a, dans la région dans laquelle s'étend la canalisation (107), une courbure en forme de V dans la direction de l'axe (A).
  8. Installation frigorifique suivant l'une des revendications précédentes, caractérisée en ce que le caloduc (105) est constitué sensiblement sous la forme d'un tronc de cône.
  9. Installation frigorifique suivant l'une des revendications précédentes, caractérisée par un système de refroidissement supplémentaire, comprenant
    a. un espace (301) de fluide réfrigérant relié à l'élément (103) de liaison froid,
    b. un conduit (302) d'entrée, par lequel l'espace (301) pour du fluide réfrigérant peut être rempli d'un deuxième fluide réfrigérant provenant d'un emplacement plus haut géodésiquement à l'extérieur du cryostat (108),
    c. un système (303) de canalisation, qui est relié, suivant une grande surface thermiquement, aux parties à refroidir du dispositif (102) et dans lequel le deuxième fluide réfrigérant peut circuler en raison d'un effet de thermosiphon et
    d. un conduit (304) d'évacuation des gaz, par lequel du deuxième fluide réfrigérant gazeux peut se dégager du système (303) de canalisation.
  10. Installation frigorifique suivant l'une des revendications précédentes, caractérisée en ce que les éléments (101, 103) de liaison sont en un matériau bon conducteur de la chaleur, en étant de préférence en cuivre.
  11. Installation frigorifique suivant l'une des revendications précédentes, caractérisée en ce que le caloduc (105) est en un matériau ayant une conductibilité thermique plus petite que celle du cuivre, en étant de préférence en acier fin.
  12. Installation frigorifique suivant l'une des revendications précédentes, caractérisée en ce que le dispositif comporte des parties supraconductrices.
  13. Installation frigorifique suivant l'une des revendications précédentes, caractérisée en ce que le dispositif est une installation à portique pour la radiothérapie.
  14. Installation frigorifique suivant la revendication 13, caractérisée en ce que les parties (102) à refroidir sont des aimants, de préférence des aimants supraconducteurs de déviation d'un faisceau de particules.
EP07803233.1A 2006-09-29 2007-09-05 Installation frigorifique comportant un élément de raccordement chaud et un élément de raccordement froid, ainsi qu'un tube échangeur de chaleur relié à ces éléments de raccordement Not-in-force EP2066991B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006046688A DE102006046688B3 (de) 2006-09-29 2006-09-29 Kälteanlage mit einem warmen und einem kalten Verbindungselement und einem mit den Verbindungselementen verbundenen Wärmerohr
PCT/EP2007/059269 WO2008040609A1 (fr) 2006-09-29 2007-09-05 Installation frigorifique comportant un élément de raccordement chaud et un élément de raccordement froid, ainsi qu'un tube échangeur de chaleur relié à ces éléments de raccordement

Publications (2)

Publication Number Publication Date
EP2066991A1 EP2066991A1 (fr) 2009-06-10
EP2066991B1 true EP2066991B1 (fr) 2017-08-16

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EP07803233.1A Not-in-force EP2066991B1 (fr) 2006-09-29 2007-09-05 Installation frigorifique comportant un élément de raccordement chaud et un élément de raccordement froid, ainsi qu'un tube échangeur de chaleur relié à ces éléments de raccordement

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KR20090077800A (ko) 2009-07-15
KR101422231B1 (ko) 2014-07-22
ES2647681T3 (es) 2017-12-26
US20090293504A1 (en) 2009-12-03
DE102006046688B3 (de) 2008-01-24
WO2008040609A1 (fr) 2008-04-10
EP2066991A1 (fr) 2009-06-10
CN101523136A (zh) 2009-09-02

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