EP2936006B1 - Refrigeration and/or liquefaction device and method thereof - Google Patents

Refrigeration and/or liquefaction device and method thereof Download PDF

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Publication number
EP2936006B1
EP2936006B1 EP13803115.8A EP13803115A EP2936006B1 EP 2936006 B1 EP2936006 B1 EP 2936006B1 EP 13803115 A EP13803115 A EP 13803115A EP 2936006 B1 EP2936006 B1 EP 2936006B1
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EP
European Patent Office
Prior art keywords
heat exchanger
working gas
auxiliary fluid
cooling
heat
Prior art date
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EP13803115.8A
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German (de)
French (fr)
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EP2936006A1 (en
Inventor
Jean-Marc Bernhardt
Fabien Durand
Vincent Heloin
Pierre BARJHOUX
Gilles FLAVIEN
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LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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Publication of EP2936006A1 publication Critical patent/EP2936006A1/en
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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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0005—Light or noble gases
    • F25J1/0007—Helium
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0275—Construction and layout of liquefaction equipments, e.g. valves, machines adapted for special use of the liquefaction unit, e.g. portable or transportable devices
    • F25J1/0276—Laboratory or other miniature devices
    • 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
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
    • F25J1/0062—Light or noble gases, mixtures thereof
    • F25J1/0065—Helium
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0262—Details of the cold heat exchange system
    • F25J1/0264—Arrangement of heat exchanger cores in parallel with different functions, e.g. different cooling streams
    • F25J1/0265—Arrangement of heat exchanger cores in parallel with different functions, e.g. different cooling streams comprising cores associated exclusively with the cooling of a refrigerant stream, e.g. for auto-refrigeration or economizer
    • F25J1/0268—Arrangement of heat exchanger cores in parallel with different functions, e.g. different cooling streams comprising cores associated exclusively with the cooling of a refrigerant stream, e.g. for auto-refrigeration or economizer using a dedicated refrigeration means
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/046—Condensers with refrigerant heat exchange tubes positioned inside or around a vessel containing water or pcm to cool the refrigerant gas
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2210/00—Processes characterised by the type or other details of the feed stream
    • F25J2210/42—Nitrogen
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/02—Bath type boiler-condenser using thermo-siphon effect, e.g. with natural or forced circulation or pool boiling, i.e. core-in-kettle heat exchanger
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/90—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration
    • F25J2270/904—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration by liquid or gaseous cryogen in an open loop
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/90—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration
    • F25J2270/912—Liquefaction cycle of a low-boiling (feed) gas in a cryocooler, i.e. in a closed-loop refrigerator
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/44—Particular materials used, e.g. copper, steel or alloys thereof or surface treatments used, e.g. enhanced surface

Definitions

  • the present invention relates to a refrigeration and / or liquefaction device and a corresponding method.
  • the invention particularly relates to helium refrigerators / liquefiers generating very low temperatures (for example 4.5K in the case of helium) in order to continuously cool users such as superconducting cables or devices of a device of plasma generation ("TOKAMAK").
  • refrigeration / liquefaction device is meant in particular refrigeration devices and / or liquefaction devices at very low temperatures (cryogenic temperatures) cooling and liquefying where appropriate a low molecular weight gas such as helium.
  • WO2011110768 A1 and WO2011117499 A1 describe methods for refrigeration in pulsed charge of an organ of a "Tokamak" in which the increase of the refrigeration power produced by the refrigeration device is automatically triggered in response to a signal produced during a start-up step of a plasma in the Tokamak.
  • the refrigeration / liquefaction device is generally unsuitable for such cooling.
  • the device comprises an auxiliary pre-cooling system which provides frigories during this cold setting.
  • the pre-cooling system generally comprises a liquid nitrogen capacity (at constant temperature, eg 80K) which supplies working gas frigories via at least one heat exchanger.
  • fluid mixtures are required between 80K helium and warmer helium (at room temperature or at the return temperature of the user to be cooled).
  • the Heat exchangers suitable for this normal operation include plate-type aluminum exchangers and brazed fins. This type of exchanger can not typically accept temperature differences between countercurrent fluids of more than 50 K.
  • An object of the present invention is to overcome all or part of the disadvantages of the prior art noted above.
  • the device comprises the pre-assembly system. cooler comprising a third heat exchanger, the first heat exchanger being of the aluminum plate and fin type, the second heat exchanger being of the tube type or of the welded plate type, this second heat exchanger being immersed in an auxiliary cooling fluid bath and in that the second and third heat exchangers are connected both in series and in parallel to the working circuit downstream of the first heat exchanger, i.e. that the working gas cooled in the first heat exchanger can be selectively admitted into the second and / or the third heat exchanger, and in that the second heat exchanger is immersed in a first liquefied auxiliary gas capacity.
  • the invention also relates to a cooling method according to claim 10 of a user using a refrigerating and / or liquefying device for a working gas according to any one of claims 1-9, wherein, user is cooled via the heat exchange system.
  • the method comprises a step of pre-cooling the user having an initial temperature of between 250 K and 400 K in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger. then is subdivided into two streams of which a first stream is cooled in the second heat exchanger and then in the third heat exchanger and a second stream is cooled directly in the third heat exchanger, the auxiliary fluid vaporized in the first capacity being discharged without give away frigories to the first heat exchanger.
  • the method comprises a step of pre-cooling the user having an initial temperature of between 250 K and 150 K in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger. heat then in the second heat exchanger and is split into two streams, a first flow is cooled in the third heat exchanger and a second flow avoids the third heat exchanger, the third heat exchanger being supplied with auxiliary fluid to transfer frigories of the auxiliary fluid to the working gas in the third exchanger, the auxiliary fluid vaporized in the first capacity and / or in contact with the third exchanger being discharged without yielding frigories to the first heat exchanger.
  • the method comprises a step of pre-cooling the user having an initial temperature of between 150K and 95K in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger. heat then in the second heat exchanger and then in the third heat exchanger, at least a portion of the auxiliary fluid vaporized in the first capacity and / or in contact with the third heat exchanger being removed by yielding frigories to the first heat exchanger.
  • the method comprises a step of pre-cooling the user having an initial temperature of between 95 K and 80 K in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger.
  • the device cools the user according to a so-called nominal operation in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger then only in the third heat exchanger, the third exchanger being supplied with auxiliary fluid to transfer frigories of the auxiliary fluid to the working gas in the third exchanger and in that the auxiliary fluid vaporized in contact with the third exchanger is evacuated by yielding frigories at the first heat exchanger.
  • the installation 100 may comprise, conventionally, a refrigeration / liquefaction device comprising a working circuit submitting helium to a work cycle to produce cold.
  • the working circuit of the refrigeration device 2 comprises a compression station 1 provided with at least one compressor 5 and preferably several compressors which provide a compression of the helium.
  • the helium enters a box 2 of cold for the cooling of the helium.
  • the cold box 2 comprises a plurality of heat exchangers which heat exchange with helium to cool the latter.
  • the cold box 2 comprises one or more turbines 7 to relax the compressed helium.
  • the cold box 2 operates according to a Brayton type thermodynamic cycle or any other appropriate cycle.
  • At least a portion of the helium is liquefied at the outlet of the cold box 2 and enters a heat exchange system 14 provided to ensure a selective heat exchange between the liquid helium and a user 10 to cool.
  • the user 10 comprises for example a magnetic field generator obtained using a superconducting magnet and / or one or more cryo-condensation pumping units or any other member requiring cooling at a very low temperature.
  • the device further comprises, in a manner known per se, an additional pre-cooling system of the working gas at the outlet of the compression station 2.
  • the pre-cooling system comprises a capacity 3 of auxiliary cryogenic fluid such as liquid nitrogen.
  • the capacitor 3 is connected to the working circuit via at least one heat exchanger for selectively transferring frigories of the auxiliary fluid to the working gas.
  • the capacitor 3 may be supplied with auxiliary fluid via a supply line 113 connected to an auxiliary fluid source (not shown) and provided with a valve 23 (cf. figure 3 ).
  • the compression station 1 comprises two compressors 11, 12 in series defining for example three pressure levels for helium.
  • the compression station 2 may also include helium purification organs 8.
  • the helium is admitted to a cold box 2 in which this helium is cooled by heat exchange with several exchangers 5 and is in which it is expanded in turbines 7.
  • the liquefied helium in the cold box 2 can be stored in a reserve 14 provided with an exchanger 144 for heat exchange with the user 10 to cool (for example via a circuit provided with a pump).
  • This heat exchange system 14 between the helium and the user 10 may comprise any other appropriate structure.
  • the low-pressure helium that has passed through the heat exchange system 14 is sent back to the compression station 1 via a return line 9 in order to restart a work cycle.
  • the relatively cold helium transfers heat to the heat exchangers and in this way cools the relatively hot helium which circulates in the opposite direction in the cold box 2 before reaching the user 10.
  • the working circuit may comprise a return line 19 returning to the station 1 for compressing the helium of the cold box 2 that has not passed through the heat exchange system 14.
  • the device comprises a pre-cooling system comprising a capacity 3 of auxiliary cryogenic fluid such as liquid nitrogen at a temperature of 80K for example.
  • auxiliary cryogenic fluid such as liquid nitrogen at a temperature of 80K for example.
  • the cold box 2 comprises a first helium cooling stage which receives the helium as soon as it leaves the compression station 1.
  • This first cooling stage comprises a first heat exchanger, a second heat exchanger and a third heat exchanger.
  • the first heat exchanger is preferably of the plate type aluminum and brazed fins.
  • Such an exchanger is, for example, in accordance with the recommendations of ALPEMA (Association of Manufacturers of Brazed Aluminum Plate and Wave Exchangers).
  • the first heat exchanger is for example of the heat exchange type between different streams of helium at different respective temperatures.
  • the first heat exchanger may comprise a first feedthrough 6 of hot and high pressure working gas coming directly from the compression station 1, a second countercurrent passage of the first passage and supplied by the gas return pipe 9. working said cold and low pressure and a third passage against the current of the first passage and fed medium pressure working gas via a return line 19.
  • the first exchanger 5 further comprises a passage section for auxiliary fluid.
  • the second 15 and third 25 heat exchangers are connected both in series and in parallel on the working circuit downstream of the first exchanger heat, that is, the working gas cooled in the first heat exchanger can be selectively admitted to the second and / or third heat exchanger.
  • the second and third heat exchangers can be connected both in series and in parallel with the first heat exchanger via a network of lines 6, 16, 26, 250 and valves 116, 126, 326 forming a parallel connection and a series link between the two heat exchangers 15, 25 and a bypass line 250 (bypass) of the second heat exchanger.
  • the second heat exchanger is preferably of the tube type (for example stainless steel, copper or other alloy compatible with cryogenic temperatures) immersed in a bath of auxiliary cooling fluid such as liquid nitrogen at 80K. More specifically, the second heat exchanger 15 is immersed in a first liquid nitrogen capacity 3. As previously described, the first capacitor 3 can be supplied with auxiliary fluid via a supply duct 113 connected to an auxiliary fluid source (not shown) and provided with a valve 23.
  • auxiliary fluid such as liquid nitrogen at 80K.
  • this second submerged heat exchanger may be a heat exchanger made of stainless steel or other welded plate metal or alloy, that is to say an exchanger whose technology is known in English under the name "Plate and Shell ".
  • These types of heat exchangers constituting the second heat exchanger are designed to withstand, without disadvantage, relatively large temperature differences between the different use configurations (immersed / non-submerged), for example temperature differences between 60 K and 250K.
  • the device comprises a first vaporized auxiliary fluid discharge conduit 30 connecting an upper end of the first capacitor to a remote auxiliary fluid recovery system via a passage in the first heat exchanger.
  • This first vaporized auxiliary fluid discharge conduit 30 also includes a selective bypass branch 130 of the first heat exchanger via a valve system 230, 430.
  • the third heat exchanger is preferably a plate-and-fin type aluminum exchanger.
  • the third exchanger 25 is of the type with selective heat exchange between helium and nitrogen.
  • the device may comprise a feed pipe 13 provided with at least one valve (not shown) connecting (for example in a loop) the first capacitor 3 to the third heat exchanger, for selectively transferring frigories of the auxiliary fluid to the working gas in the third heat exchanger.
  • the figure 3 illustrates an alternative embodiment of the first cooling stage of the device.
  • the embodiment of the figure 3 differs from that of the figure 2 only in that the third heat exchanger 25 is this time immersed in a second capacity 33 of auxiliary fluid (instead of being supplied with auxiliary fluid from the first capacity 3 or from a source).
  • this second fluid capacity 33 may be a cryogenic tank selectively supplied with auxiliary fluid by a source of auxiliary fluid.
  • the third heat exchanger is immersed in said second capacitor 33 to allow, if appropriate, an exchange of frigories between the working gas and the auxiliary fluid of the second capacitor 33.
  • the second auxiliary capacity 33 also includes a second vaporized auxiliary fluid discharge conduit 330 connecting an upper end of the second capacity to a remote auxiliary fluid recovery system via a passage in the first heat exchanger.
  • the second discharge pipe 330 connects to the first auxiliary fluid discharge pipe 30, upstream of the first heat exchanger 5. That is to say that the auxiliary fluid vaporized in the second capacitor 33 can be distributed between a passage in the first exchanger 5 and / or line 130 bypass avoiding this first 5 heat exchanger.
  • the Figures 4 to 7 respectively illustrate four distinct configurations that can be used during a succession of an example of possible operation of the device.
  • a first phase of cooling a user 10 illustrated in the figure 4 the helium leaving the compression station 1 is cooled by heat exchange in the first heat exchanger and the cooled helium is divided into two streams (valves 116 and 126 open). A first of these two streams is cooled in the second heat exchanger and then passes into the third heat exchanger without heat exchange (valve 233 closed). The second stream does not pass into the second heat exchanger and is mixed with the first outflow of the second heat exchanger 15 before passing into the third heat exchanger.
  • the first capacity 3 is supplied with auxiliary fluid (nitrogen) and the vaporized nitrogen is evacuated via the evacuation pipe 30 and the bypass branch 130 without yielding frigories to the first heat exchanger 5 ( valve 230 open in branch branch 130 and valve 430 closed for passage through the first exchanger 5).
  • auxiliary fluid nitrogen
  • a second phase of cooling a user 10 illustrated in FIG. figure 5 the helium leaving the compression station 1 can be cooled by heat exchange in the first heat exchanger and then in the second heat exchanger (valve 116 open and valve 126 closed).
  • the helium is then split into two streams of which a first stream is cooled in the third heat exchanger and a second stream which passes through the bypass line 250 (opening of the valve 326 in the bypass line 250 ).
  • the first 3 and the second capacitor 33 are supplied with auxiliary fluid via respective supply lines 113, 133 (corresponding open valves 213 and 233).
  • Auxiliary fluids vaporized in the capacitors 3, 33 can be evacuated without passing through the first heat exchanger 5, that is to say via the branch 130 of bypass (valve 430 closed and valve 230 open).
  • a third cooling phase of a user 10 illustrated in FIG. figure 6 the working gas leaving the compression station 1 can be cooled in series by heat exchange in the first heat exchanger and then in the second heat exchanger and then in the third heat exchanger (valve 116 open, valve 126 closed).
  • the auxiliary fluid vaporized in the first 3 and second 33 capacities can be discharged partly via the first heat exchanger and partly via the branch 130 bypass (valve 230 and 430 open).
  • a fourth cooling phase of a user 10 illustrated in FIG. figure 7 the working gas exiting the compression station 1 can be cooled in series by heat exchange in the first heat exchanger and then in the third heat exchanger (without passing through the second heat exchanger: valve 116 closed and valve 126 open). Only the second capacitor 33 may be supplied with auxiliary fluid (valve 213 closed and valve 233 open). The auxiliary fluid vaporized in the second capacity 33 can be discharged partly via the first heat exchanger and partly via the branch 130 bypass (valve 230 and 430 open).
  • the device can ensure continuous cooling (keeping cold at the determined temperature) with the same device.
  • the device can also function according to the configuration of the figure 7 . That is, the working gas exiting the compression station 1 can be cooled in series by heat exchange in the first heat exchanger and then in the third heat exchanger (without passing through the second heat exchanger 15). of heat) and only the second capacitor 33 can be supplied with auxiliary fluid.
  • the auxiliary fluid vaporized in the second capacity can be discharged via the first heat exchanger (valve 230 closed and valve 430 open).
  • the architectures described above thus make it possible to cool a massive component of a relatively hot temperature (for example 400K at a relatively low temperature (for example 80K) with a reduced number of equipment.
  • first and third heat exchangers two plate and fin type aluminum exchangers
  • second exchanger 15 a tube type heat exchanger
  • Another advantage provided by the device is to limit the heat input to the working gas in normal operation by isolating the circuits and equipment used only for cooling. This equipment can be installed outside the cold box and it also reduces the size and cost of the enclosure of the cold box.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Health & Medical Sciences (AREA)
  • Clinical Laboratory Science (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Description

La présente invention concerne un dispositif de réfrigération et/ou de liquéfaction ainsi qu'un procédé correspondant.The present invention relates to a refrigeration and / or liquefaction device and a corresponding method.

L'invention concerne un dispositif de réfrigération et/ou liquéfaction d'un gaz de travail comprenant de l'hélium ou constitué d'hélium pur, le dispositif comprenant un circuit de travail en boucle pour le gaz de travail comportant, en série :

  • une station de compression du gaz de travail munie d'au moins un compresseur,
  • une boîte froide pour refroidir le gaz de travail comprenant une pluralité d'échangeurs de chaleur disposés en série et au moins un organe de détente du gaz de travail,
  • un système d'échange thermique entre le gaz de travail refroidi et un utilisateur,
au moins une conduite de retour dans la station de compression pour le gaz de travail ayant transité dans le système d'échange thermique, la conduite de retour comprenant au moins un échangeur de réchauffage du gaz de travail, le dispositif comprenant en outre un système de pré-refroidissement additionnel du gaz de travail en sortie de la station de compression, le système de pré-refroidissement comprenant au moins une capacité de fluide cryogénique auxiliaire tel que de l'azote liquide, la capacité étant reliée au circuit de travail via au moins un échangeur de chaleur pour transférer sélectivement des frigories du fluide auxiliaire vers le gaz de travail, la boîte froide comprenant un premier étage de refroidissement du gaz de travail comportant un premier échangeur disposé à la sortie de la station de compression ainsi qu'un second échangeur de chaleur.The invention relates to a device for refrigerating and / or liquefying a working gas comprising helium or consisting of pure helium, the device comprising a loop work circuit for the working gas comprising, in series:
  • a compressor station for the working gas provided with at least one compressor,
  • a cold box for cooling the working gas comprising a plurality of heat exchangers arranged in series and at least one expansion member of the working gas,
  • a heat exchange system between the cooled working gas and a user,
at least one return line in the compressor station for the working gas having passed through the heat exchange system, the return line comprising at least one working gas reheating exchanger, the device further comprising a additional pre-cooling of the working gas at the outlet of the compression station, the pre-cooling system comprising at least one auxiliary cryogenic fluid capacity such as liquid nitrogen, the capacity being connected to the working circuit via at least one a heat exchanger for selectively transferring frigories of the auxiliary fluid to the working gas, the cold box comprising a first working gas cooling stage having a first exchanger disposed at the outlet of the compressor station and a second exchanger heat.

L'invention concerne notamment les réfrigérateurs/liquéfacteurs à hélium générant des températures très basses (par exemple 4,5K pour le cas de l'hélium) en vue de refroidir en continu des utilisateurs tels que des câbles supraconducteurs ou des organes d'un dispositif de génération de plasma (« TOKAMAK »). Par dispositif de réfrigération/liquéfaction, on désigne notamment les dispositifs de réfrigération et/ou les dispositifs de liquéfaction à très basse température (températures cryogéniques) refroidissant et liquéfiant le cas échéant un gaz à faible masse molaire tel que de l'hélium.The invention particularly relates to helium refrigerators / liquefiers generating very low temperatures (for example 4.5K in the case of helium) in order to continuously cool users such as superconducting cables or devices of a device of plasma generation ("TOKAMAK"). By refrigeration / liquefaction device is meant in particular refrigeration devices and / or liquefaction devices at very low temperatures (cryogenic temperatures) cooling and liquefying where appropriate a low molecular weight gas such as helium.

Les documents WO2011110768 A1 et WO2011117499 A1 décrivent des procédés de réfrigération en charge pulsée d'un organe d'un « Tokamak » dans lequel l'augmentation de la puissance de réfrigération produite par le dispositif de réfrigération est déclenchée automatiquement en réponse à un signal produit lors d'une étape de démarrage d'un plasma dans le Tokamak.The documents WO2011110768 A1 and WO2011117499 A1 describe methods for refrigeration in pulsed charge of an organ of a "Tokamak" in which the increase of the refrigeration power produced by the refrigeration device is automatically triggered in response to a signal produced during a start-up step of a plasma in the Tokamak.

Le document US2009094992 A1 décrit un refroidisseur cryogénique pour liquéfier du gaz dans le col d'un cryostat.The document US2009094992 A1 describes a cryogenic cooler for liquefying gas in the neck of a cryostat.

Lors de la mise en froid de l'utilisateur, c'est-à-dire lorsque l'utilisateur doit être amené d'une température de départ relativement élevée (par exemple 300K ou au-dessus) jusqu'à une température basse déterminée de fonctionnement nominal (par exemple autour de 80K). Le dispositif de réfrigération/liquéfaction est généralement peu adapté à une telle mise en froid.When the user is cold, that is to say when the user must be brought from a relatively high starting temperature (for example 300K or above) to a determined low temperature of nominal operation (for example around 80K). The refrigeration / liquefaction device is generally unsuitable for such cooling.

En effet, lors de la mise en froid de composants lourds (comme des aimants surpra-conducteurs par exemple) de la température ambiante jusqu'à 80K sur une grande période (pendant quelques dizaines de jours), des flux d'hélium relativement chaud et froid (alimentation en direction de l'utilisateur et retour de l'utilisateur) transitent à contre-courant dans des échangeurs communs. Pour le bon fonctionnement du dispositif, il est cependant nécessaire de limiter l'écart de température entre ces flux d'hélium (par exemple entre 40K et 50K d'écart au maximum).Indeed, during the cooling of heavy components (such as super-conductive magnets for example) from ambient temperature up to 80K over a large period (for a few tens of days), relatively hot helium flows and cold (power supply to the user and return of the user) flow against the current in common exchangers. For the proper functioning of the device, however, it is necessary to limit the temperature difference between these helium flows (for example between 40K and 50K maximum difference).

A cet effet le dispositif comporte un système de pré-refroidissement auxiliaire qui fournit des frigories pendant cette mise en froid.For this purpose the device comprises an auxiliary pre-cooling system which provides frigories during this cold setting.

Comme illustré notamment dans l'article (« Solutions for liquid nitrogen pre-cooling in helium refrigeration cycles » de U. Wagner du CERN - 2000), le système de pré-refroidissement comprend généralement une capacité d'azote liquide (à température constante, par exemple 80K) qui fournit des frigories au gaz de travail via au moins un échangeur de chaleur.As illustrated in particular in the article (U. Wagner's "Solutions for liquid nitrogen pre-cooling in helium refrigeration cycles" of CERN - 2000), the pre-cooling system generally comprises a liquid nitrogen capacity (at constant temperature, eg 80K) which supplies working gas frigories via at least one heat exchanger.

Ces systèmes connus de pré-refroidissement présentent cependant des contraintes ou inconvénients.These known pre-cooling systems, however, have constraints or disadvantages.

Ainsi, des mélanges de fluides sont nécessaires entre de l'hélium à 80K et de l'hélium plus chaud (à la température ambiante ou à la température de retour de l'utilisateur à refroidir).Thus, fluid mixtures are required between 80K helium and warmer helium (at room temperature or at the return temperature of the user to be cooled).

Pour limiter la consommation d'azote liquide il est par ailleurs nécessaire de récupérer les frigories de l'hélium qui revient de l'utilisateur à refroidir au fur et à mesure de son refroidissement. Ces contraintes d'écart de température et de performance nécessitent des technologies d'échangeurs de chaleur différentes en fonction des différentes configurations de fonctionnement (mise en froid, fonctionnement normal).To limit the consumption of liquid nitrogen it is also necessary to recover the frigories of helium which is returned by the user to cool as it cools. These temperature and performance deviation constraints require different heat exchanger technologies depending on the different operating configurations (cooling, normal operation).

Ainsi, pendant l'opération normale (hors de la phase de mise en froid), les échangeurs doivent être très performants, c'est-à-dire avoir de faibles pertes de charge et ne doivent pas être confrontés à des écarts de température importants. Les échangeurs de chaleurs adaptés pour ce fonctionnement normal comprennent des échangeurs de type en aluminium à plaque et ailettes brasées. Ce type d'échangeur ne peut typiquement accepter des écarts de température entre fluides à contre courant de plus 50 K.Thus, during the normal operation (out of the cooling phase), the exchangers must be very efficient, that is to say have low pressure losses and must not be confronted with significant temperature differences. . The Heat exchangers suitable for this normal operation include plate-type aluminum exchangers and brazed fins. This type of exchanger can not typically accept temperature differences between countercurrent fluids of more than 50 K.

Pendant la mise en froid d'utilisateurs massifs, la performance de l'échange thermique requis dans les échangeurs est moins importante mais reste élevée. En revanche, les écarts de température (du fait de l'azote liquide à température constante) deviennent relativement importants (supérieurs à 50K).During the chilling of massive users, the performance of the heat exchange required in the exchangers is less important but remains high. On the other hand, temperature differences (due to liquid nitrogen at constant temperature) become relatively large (greater than 50K).

Lorsque les températures de l'hélium sont encore élevées dans les circuits et échangeurs, la perte de charge est bien supérieure à celle requise en fonctionnement normal.When helium temperatures are still high in the circuits and exchangers, the pressure drop is much higher than that required during normal operation.

Des solutions existantes pour résoudre ces problèmes nécessitent un échangeur principal à l'entrée de la boîte froide qui assure un échange thermique entre l'hélium et l'azote. D'autres solutions prévoient de scinder cet échangeur principal en plusieurs sections indépendantes réalisées dans des technologies d'échangeurs différentes selon la nature du fluide (hélium ou azote).Existing solutions to solve these problems require a main heat exchanger at the inlet of the cold box which ensures a heat exchange between helium and nitrogen. Other solutions include splitting the main heat exchanger into several independent sections made in different heat exchanger technologies depending on the nature of the fluid (helium or nitrogen).

Ces solutions ne résolvent pas de façon satisfaisante les problèmes car le dispositif est soit mal adapté au fonctionnement normal, soit mal adapté à la phase de mise en froid.These solutions do not satisfactorily solve the problems because the device is either poorly adapted to normal operation or poorly adapted to the cooling phase.

Le document FR 2919713 A1 , considéré l'art antérieur le plus proche, décrit un dispositif conforme au préambule de la revendication 1.The document FR 2919713 A1 , considered the closest prior art, describes a device according to the preamble of claim 1.

Un but de la présente invention est de pallier tout ou partie des inconvénients de l'art antérieur relevés ci-dessus.An object of the present invention is to overcome all or part of the disadvantages of the prior art noted above.

A cette fin, le dispositif selon l'invention, par ailleurs conforme à la définition générique qu'en donne le préambule ci-dessus, est défini par la revendication 1. C'est-à-dire que le dispositif comporte le système de pré-refroidissement comprenant un troisième échangeur de chaleur, le premier échangeur de chaleur étant du type en aluminium à plaque et ailettes, le second échangeur de chaleur étant du type à tube(s) ou du type à plaques soudées, ce second échangeur de chaleur étant immergé dans un bain de fluide auxiliaire de refroidissement et en ce que les second et troisième échangeurs de chaleur sont raccordés à la fois en série et en parallèle sur le circuit de travail en aval du premier échangeur de chaleur, c'est-à-dire que le gaz de travail refroidi dans le premier échangeur de chaleur peut être admis sélectivement dans le second et/ou dans le troisième échangeur de chaleur, et en ce que le second échangeur de chaleur est immergé dans une première capacité de gaz auxiliaire liquéfié.To this end, the device according to the invention, furthermore in conformity with the generic definition given in the preamble above, is defined by claim 1. That is to say that the device comprises the pre-assembly system. cooler comprising a third heat exchanger, the first heat exchanger being of the aluminum plate and fin type, the second heat exchanger being of the tube type or of the welded plate type, this second heat exchanger being immersed in an auxiliary cooling fluid bath and in that the second and third heat exchangers are connected both in series and in parallel to the working circuit downstream of the first heat exchanger, i.e. that the working gas cooled in the first heat exchanger can be selectively admitted into the second and / or the third heat exchanger, and in that the second heat exchanger is immersed in a first liquefied auxiliary gas capacity.

Par ailleurs, des modes de réalisation de l'invention peuvent comporter l'une ou plusieurs des caractéristiques suivantes :

  • le second échangeur de chaleur est l'un parmi : un échangeur de chaleur de type à tubes en inox ou aluminium, un échangeur de chaleur de type à tube à ailettes en inox ou aluminium, un échangeur à plaques soudées en inox,
  • le circuit comprend une branche de by-pass sélectif du troisième échangeur de chaleur permettant sélectivement au gaz de travail issu du premier et/ou du second échangeur de chaleur d'éviter le troisième échangeur de chaleur dans le circuit de travail,
  • le dispositif comporte une première conduite d'évacuation de fluide auxiliaire vaporisé reliant une extrémité supérieure de la première capacité à un système de récupération de fluide auxiliaire déporté via un passage dans le premier échangeur de chaleur,
  • la première conduite d'évacuation de fluide auxiliaire vaporisé comprend une branche de by-pass sélectif du premier échangeur de chaleur,
  • le troisième échangeur est du type à échange de chaleur sélectif entre le gaz de travail et le fluide auxiliaire, le dispositif comprenant une conduite d'alimentation sélectif reliant la première capacité au troisième échangeur de chaleur, pour transférer des frigories du fluide auxiliaire vers le gaz de travail dans le troisième échangeur de chaleur,
  • le dispositif comporte une seconde capacité de fluide sélectivement alimentée en fluide auxiliaire par une source de fluide auxiliaire et en ce que le troisième échangeur de chaleur est immergé dans ladite seconde capacité pour permettre un échange de frigories entre le gaz de travail et le fluide auxiliaire de la seconde capacité,
  • le dispositif comporte une seconde conduite d'évacuation de fluide auxiliaire vaporisé reliant une extrémité supérieure de la seconde capacité à un système de récupération de fluide auxiliaire déporté via un passage dans le premier échangeur de chaleur,
  • la seconde conduite d'évacuation de fluide auxiliaire vaporisé comprend une branche de by-pass sélectif du premier échangeur de chaleur,
  • le second et le troisième échangeurs de chaleur sont raccordés via un réseau de conduites et de vannes formant la liaison en parallèle et la liaison en série entre les deux échangeurs de chaleur ainsi qu'une ligne de by-pass (c'est-à-dire de dérivation) du second échangeur de chaleur,
  • la première capacité est sélectivement alimentée en fluide auxiliaire via une conduite d'amenée reliée à une source de fluide auxiliaire et munie d'une vanne,
  • le premier échangeur de chaleur est du type à échange de chaleur entre des flux différents de gaz de travail à des températures respectives différentes et comprend un premier passage alimentée en gaz de travail dit chaud et à haute pression sortant de la station de compression, un second passage à contre-courant du premier passage et alimenté par la conduite de retour en gaz de travail dit froid et à basse pression et un troisième passage à contre-courant du premier passage et alimenté en gaz de travail dit à moyenne pression via une conduite de renvoi du circuit de travail renvoyant du gaz de travail à partir de la boîte froide n'ayant pas transité dans le système d'échange thermique,
Furthermore, embodiments of the invention may include one or more of the following features:
  • the second heat exchanger is one of: a stainless steel or aluminum tube type heat exchanger, a stainless steel or aluminum finned tube type heat exchanger, a stainless steel welded plate heat exchanger,
  • the circuit comprises a selective bypass branch of the third heat exchanger selectively allowing the working gas from the first and / or the second heat exchanger to avoid the third heat exchanger in the working circuit,
  • the device comprises a first vaporized auxiliary fluid discharge line connecting an upper end of the first capacity to a remote auxiliary fluid recovery system via a passage in the first heat exchanger,
  • the first vaporized auxiliary fluid discharge conduit comprises a selective bypass branch of the first heat exchanger,
  • the third exchanger is of the selective heat exchange type between the working gas and the auxiliary fluid, the device comprising a selective supply line connecting the first capacity to the third heat exchanger, for transferring frigories of the auxiliary fluid to the gas working in the third heat exchanger,
  • the device comprises a second fluid capacity selectively supplied with auxiliary fluid by a source of auxiliary fluid and in that the third heat exchanger is immersed in said second capacity to allow an exchange of frigories between the working gas and the auxiliary fluid of the second ability,
  • the device comprises a second vaporized auxiliary fluid discharge line connecting an upper end of the second capacity to a remote auxiliary fluid recovery system via a passage in the first heat exchanger,
  • the second vaporized auxiliary fluid discharge conduit comprises a selective bypass branch of the first heat exchanger,
  • the second and the third heat exchangers are connected via a network of pipes and valves forming the parallel connection and the series connection between the two heat exchangers and a bypass line (i.e. bypass) of the second heat exchanger,
  • the first capacity is selectively supplied with auxiliary fluid via a supply line connected to a source of auxiliary fluid and provided with a valve,
  • the first heat exchanger is of the heat exchange type between different flows of working gas at different respective temperatures and comprises a first passage supplied with hot and high pressure working gas leaving the compression station, a second countercurrent passage of the first passage and fed by the return line in working gas said cold and low pressure and a third passage against the current of the first passage and supplied with working gas said medium pressure via a pipe of return of the working circuit returning working gas from the cold box that has not passed through the heat exchange system,

L'invention concerne également un procédé de refroidissement selon la revendication 10 d'un utilisateur utilisant un dispositif de réfrigération et/ou de liquéfaction d'un gaz de travail conforme à l'une quelconque des revendications 1-9, dans lequel, l'utilisateur est refroidi via le système d'échange thermique. Dans un mode de développement le procédé comporte une étape de pré-refroidissement de l'utilisateur ayant une température initiale comprise entre 250K et 400K dans laquelle le gaz de travail sortant de la station de compression est refroidi par échange thermique dans le premier échangeur de chaleur puis est subdivisé en deux flux dont un premier flux est refroidi dans le second échangeur de chaleur puis dans le troisième échangeur de chaleur et un deuxième flux est refroidi directement dans le troisième échangeur de chaleur, le fluide auxiliaire vaporisé dans la première capacité étant évacué sans céder des frigories au premier échangeur de chaleur. Dans un autre mode de développement le procédé comporte une étape de pré-refroidissement de l'utilisateur ayant une température initiale comprise entre 250K et 150K dans laquelle le gaz de travail sortant de la station de compression est refroidi par échange thermique dans le premier échangeur de chaleur puis dans le second échangeur de chaleur puis est scindé en deux flux dont un premier flux est refroidi dans le troisième échangeur de chaleur et un second flux évite le troisième échangeur, le troisième échangeur étant alimenté en fluide auxiliaire pour transférer des frigories du fluide auxiliaire au gaz de travail dans le troisième échangeur, le fluide auxiliaire vaporisé dans la première capacité et/ou au contact du troisième échangeur étant évacué sans céder des frigories au premier échangeur de chaleur. Dans un autre mode de développement le procédé comporte une étape de pré-refroidissement de l'utilisateur ayant une température initiale comprise entre 150K et 95K dans laquelle le gaz de travail sortant de la station de compression est refroidi par échange thermique dans le premier échangeur de chaleur puis dans le second échangeur de chaleur puis dans le troisième échangeur de chaleur, au moins une partie du fluide auxiliaire vaporisé dans la première capacité et/ou au contact du troisième échangeur étant évacué en cédant des frigories au premier échangeur de chaleur. Dans un autre mode de développement le procédé comporte une étape de pré-refroidissement de l'utilisateur ayant une température initiale comprise entre 95K et 80K dans laquelle le gaz de travail sortant de la station de compression est refroidi par échange thermique dans le premier échangeur de chaleur puis uniquement dans le troisième échangeur de chaleur, le fluide auxiliaire vaporisé au contact du troisième échangeur étant évacué en cédant des frigories au premier échangeur de chaleur. Dans un autre mode de développement, après une phase de pré-refroidissement éventuel, le dispositif refroidit l'utilisateur selon un fonctionnement dit nominal dans lequel le gaz de travail sortant de la station de compression est refroidi par échange thermique dans le premier échangeur de chaleur puis uniquement dans le troisième échangeur de chaleur, le troisième échangeur étant alimenté en fluide auxiliaire pour transférer des frigories du fluide auxiliaire au gaz de travail dans le troisième échangeur et en ce le fluide auxiliaire vaporisé au contact du troisième échangeur est évacué en cédant des frigories au premier échangeur de chaleur.The invention also relates to a cooling method according to claim 10 of a user using a refrigerating and / or liquefying device for a working gas according to any one of claims 1-9, wherein, user is cooled via the heat exchange system. In one mode of development, the method comprises a step of pre-cooling the user having an initial temperature of between 250 K and 400 K in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger. then is subdivided into two streams of which a first stream is cooled in the second heat exchanger and then in the third heat exchanger and a second stream is cooled directly in the third heat exchanger, the auxiliary fluid vaporized in the first capacity being discharged without give away frigories to the first heat exchanger. In another mode of development, the method comprises a step of pre-cooling the user having an initial temperature of between 250 K and 150 K in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger. heat then in the second heat exchanger and is split into two streams, a first flow is cooled in the third heat exchanger and a second flow avoids the third heat exchanger, the third heat exchanger being supplied with auxiliary fluid to transfer frigories of the auxiliary fluid to the working gas in the third exchanger, the auxiliary fluid vaporized in the first capacity and / or in contact with the third exchanger being discharged without yielding frigories to the first heat exchanger. In another mode of development the method comprises a step of pre-cooling the user having an initial temperature of between 150K and 95K in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger. heat then in the second heat exchanger and then in the third heat exchanger, at least a portion of the auxiliary fluid vaporized in the first capacity and / or in contact with the third heat exchanger being removed by yielding frigories to the first heat exchanger. In another mode of development, the method comprises a step of pre-cooling the user having an initial temperature of between 95 K and 80 K in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger. heat then only in the third heat exchanger, the auxiliary fluid vaporized in contact with the third heat exchanger being removed by yielding frigories to the first heat exchanger. In another mode of development, after a possible pre-cooling phase, the device cools the user according to a so-called nominal operation in which the working gas leaving the compression station is cooled by heat exchange in the first heat exchanger then only in the third heat exchanger, the third exchanger being supplied with auxiliary fluid to transfer frigories of the auxiliary fluid to the working gas in the third exchanger and in that the auxiliary fluid vaporized in contact with the third exchanger is evacuated by yielding frigories at the first heat exchanger.

D'autres particularités et avantages apparaîtront à la lecture de la description ci-après, faite en référence aux figures dans lesquelles :

  • la figure 1 représente une vue simplifiée, schématique et partielle, illustrant la structure d'un dispositif de liquéfaction/réfrigération utilisé pour refroidir un organe utilisateur,
  • la figure 2 représente de façon schématique et partielle, un premier exemple de structure et de fonctionnement d'un dispositif de liquéfaction/réfrigération utilisé pour refroidir un organe utilisateur,
  • la figure 3 représente de façon schématique et partielle un détail de la boîte froide d'un dispositif de liquéfaction/réfrigération selon un second exemple de réalisation,
  • les figures 4 à 7 représentent le détail de la figure 3 selon respectivement différentes configurations de fonctionnement distinctes.
Other particularities and advantages will appear on reading the following description, made with reference to the figures in which:
  • the figure 1 represents a simplified, schematic and partial view illustrating the structure of a liquefaction / refrigeration device used to cool a user organ,
  • the figure 2 represents schematically and partially, a first example of structure and operation of a liquefaction / refrigeration device used to cool a user organ,
  • the figure 3 schematically and partially shows a detail of the cold box of a liquefaction / refrigeration device according to a second embodiment,
  • the Figures 4 to 7 represent the detail of the figure 3 according to respective different operating configurations.

Comme représenté à la figure 1, l'installation 100 peut comprendre, classiquement, un dispositif de réfrigération/liquéfaction comprenant un circuit de travail soumettant de l'hélium à un cycle de travail pour produire du froid. Le circuit de travail du dispositif de réfrigération 2 comprend une station 1 de compression munie d'au moins un compresseur 5 et de préférence plusieurs compresseurs qui assurent une compression de l'hélium.As represented in figure 1 , the installation 100 may comprise, conventionally, a refrigeration / liquefaction device comprising a working circuit submitting helium to a work cycle to produce cold. The working circuit of the refrigeration device 2 comprises a compression station 1 provided with at least one compressor 5 and preferably several compressors which provide a compression of the helium.

En sortie de la station de la station 1 de compression, l'hélium entre dans une boite 2 de froide pour le refroidissement de l'hélium. La boîte 2 froide comprend plusieurs échangeurs 5 de chaleur qui échangent thermiquement avec l'hélium pour refroidir ce dernier. De plus, la boîte 2 froide comprend une ou plusieurs turbines 7 pour détendre l'hélium compressé. De préférence, la boite 2 froide fonctionne selon un cycle thermodynamique de type Brayton ou tout autre cycle approprié. Au moins une partie de l'hélium est liquéfié à la sortie de la boîte 2 froide et entre dans un système 14 d'échange thermique prévu pour assurer un échange thermique sélectif entre l'hélium liquide et un utilisateur 10 à refroidir. L'utilisateur 10 comprend par exemple un générateur de champ magnétique obtenu à l'aide d'un aimant supraconducteur et/ou une ou des unités de pompage par cryo-condensation ou tout autre organe nécessitant un refroidissement à très basse température.At the exit of the station of the compression station 1, the helium enters a box 2 of cold for the cooling of the helium. The cold box 2 comprises a plurality of heat exchangers which heat exchange with helium to cool the latter. In addition, the cold box 2 comprises one or more turbines 7 to relax the compressed helium. Preferably, the cold box 2 operates according to a Brayton type thermodynamic cycle or any other appropriate cycle. At least a portion of the helium is liquefied at the outlet of the cold box 2 and enters a heat exchange system 14 provided to ensure a selective heat exchange between the liquid helium and a user 10 to cool. The user 10 comprises for example a magnetic field generator obtained using a superconducting magnet and / or one or more cryo-condensation pumping units or any other member requiring cooling at a very low temperature.

Comme schématisé à la figure 1, le dispositif comprend en outre, de façon connue en soit, un système de pré-refroidissement additionnel du gaz de travail en sortie de la station 2 de compression. Le système de pré-refroidissement comprend une capacité 3 de fluide cryogénique auxiliaire tel que de l'azote liquide. La capacité 3 est reliée au circuit de travail via au moins un échangeur de chaleur pour transférer sélectivement des frigories du fluide auxiliaire vers le gaz de travail.As schematized at figure 1 the device further comprises, in a manner known per se, an additional pre-cooling system of the working gas at the outlet of the compression station 2. The pre-cooling system comprises a capacity 3 of auxiliary cryogenic fluid such as liquid nitrogen. The capacitor 3 is connected to the working circuit via at least one heat exchanger for selectively transferring frigories of the auxiliary fluid to the working gas.

Par exemple, la capacité 3 peut être alimentée en fluide auxiliaire via une conduite 113 d'amenée reliée à une source de fluide auxiliaire (non représentée) et munie d'une vanne 23 (cf. figure 3).For example, the capacitor 3 may be supplied with auxiliary fluid via a supply line 113 connected to an auxiliary fluid source (not shown) and provided with a valve 23 (cf. figure 3 ).

Dans l'exemple plus détaillé de la figure 2, la station 1 de compression comporte deux compresseurs 11, 12 en série définissant par exemple trois niveaux de pression pour l'hélium. Comme schématisé, la station 2 de compression peut comporter également des organes 8 de purification de l'hélium.In the more detailed example of the figure 2 , the compression station 1 comprises two compressors 11, 12 in series defining for example three pressure levels for helium. As shown schematically, the compression station 2 may also include helium purification organs 8.

A la sortie de la station 1 de compression, l'hélium est admis dans une boîte 2 froide dans laquelle cet hélium est refroidi par échange thermique avec plusieurs échangeurs 5 et est dans laquelle il est détendu dans des turbines 7.At the exit of the compression station 1, the helium is admitted to a cold box 2 in which this helium is cooled by heat exchange with several exchangers 5 and is in which it is expanded in turbines 7.

L'hélium liquéfié dans la boite 2 froide peut être stocké dans une réserve 14 munie d'un échangeur 144 destiné à échanger thermiquement avec l'utilisateur 10 à refroidir (par exemple via un circuit muni d'une pompe). Ce système 14 d'échange thermique entre l'hélium et l'utilisateur 10 peut comporter toute autre structure appropriée.The liquefied helium in the cold box 2 can be stored in a reserve 14 provided with an exchanger 144 for heat exchange with the user 10 to cool (for example via a circuit provided with a pump). This heat exchange system 14 between the helium and the user 10 may comprise any other appropriate structure.

L'hélium à basse pression ayant transité dans le système 14 d'échange thermique est renvoyé vers la station 1 de compression via une conduite 9 de retour en vue de recommencer un cycle de travail. Lors de ce retour, l'hélium relativement froid cède des frigories aux échangeurs 5 de chaleur et de cette façon assure le refroidissement de l'hélium relativement chaud qui circule en sens inverse dans la boîte 2 froide avant d'atteindre l'utilisateur 10.The low-pressure helium that has passed through the heat exchange system 14 is sent back to the compression station 1 via a return line 9 in order to restart a work cycle. During this return, the relatively cold helium transfers heat to the heat exchangers and in this way cools the relatively hot helium which circulates in the opposite direction in the cold box 2 before reaching the user 10.

Comme illustré, le circuit de travail peut comporter une conduite 19 de renvoi renvoyant vers la station 1 de compression de l'hélium de la boîte froide 2 n'ayant pas transité dans le système 14 d'échange thermique.As illustrated, the working circuit may comprise a return line 19 returning to the station 1 for compressing the helium of the cold box 2 that has not passed through the heat exchange system 14.

Comme visible à la figure 2, le dispositif comprend un système de pré-refroidissement comprenant une capacité 3 de fluide cryogénique auxiliaire tel que de l'azote liquide à une température de 80K par exemple.As visible at figure 2 , the device comprises a pre-cooling system comprising a capacity 3 of auxiliary cryogenic fluid such as liquid nitrogen at a temperature of 80K for example.

La boîte 2 froide comprend un premier étage de refroidissement de l'hélium qui reçoit l'hélium dès sa sortie de la station 1 de compression.The cold box 2 comprises a first helium cooling stage which receives the helium as soon as it leaves the compression station 1.

Ce premier étage de refroidissement comporte un premier 5 échangeur de chaleur, un second 15 échangeur de chaleur ainsi qu'un troisième 25 échangeur de chaleur.This first cooling stage comprises a first heat exchanger, a second heat exchanger and a third heat exchanger.

Le premier 5 échangeur de chaleur est de préférence du type en aluminium à plaque et ailettes brasées. Un tel échangeur est par exemple conforme aux recommandations de l'ALPEMA (Association des Fabricants d'Echangeurs à Plaques et Ondes en Aluminium brasées).The first heat exchanger is preferably of the plate type aluminum and brazed fins. Such an exchanger is, for example, in accordance with the recommendations of ALPEMA (Association of Manufacturers of Brazed Aluminum Plate and Wave Exchangers).

Le premier 5 échangeur de chaleur est par exemple du type à échange de chaleur entre des flux différents d'hélium à des températures respectives différentes. Le premier 5 échangeur peut comporter un premier passage alimentée 6 en gaz de travail dit chaud et à haute pression sortant directement de la station 1 de compression, un second passage à contre-courant du premier passage et alimenté par la conduite 9 de retour en gaz de travail dit froid et à basse pression et un troisième passage à contre-courant du premier passage et alimenté en gaz de travail dit à moyenne pression via une conduite 19 de renvoi. Comme décrit ci-après, le premier échangeur 5 comporte en outre une section de passage pour du fluide auxiliaire.The first heat exchanger is for example of the heat exchange type between different streams of helium at different respective temperatures. The first heat exchanger may comprise a first feedthrough 6 of hot and high pressure working gas coming directly from the compression station 1, a second countercurrent passage of the first passage and supplied by the gas return pipe 9. working said cold and low pressure and a third passage against the current of the first passage and fed medium pressure working gas via a return line 19. As described below, the first exchanger 5 further comprises a passage section for auxiliary fluid.

Les second 15 et troisième 25 échangeurs de chaleur sont raccordés à la fois en série et en parallèle sur le circuit de travail en aval du premier 5 échangeur de chaleur, c'est-à-dire que le gaz de travail refroidi dans le premier 5 échangeur de chaleur pet être admis sélectivement dans le second 15 et/ou dans le troisième 25 échangeur de chaleur.The second 15 and third 25 heat exchangers are connected both in series and in parallel on the working circuit downstream of the first exchanger heat, that is, the working gas cooled in the first heat exchanger can be selectively admitted to the second and / or third heat exchanger.

Comme représenté plus en détail à la figure 3, le second 15 et le troisième 25 échangeurs de chaleur peuvent être raccordés à la fois en série et en parallèle au premier 5 échangeur de chaleur via un réseau de conduites 6, 16, 26, 250 et de vannes 116, 126, 326 formant une liaison en parallèle et une liaison en série entre les deux échangeurs 15, 25 de chaleur ainsi qu'une ligne 250 de by-pass (dérivation) du second 15 échangeur de chaleur.As shown in more detail at figure 3 the second and third heat exchangers can be connected both in series and in parallel with the first heat exchanger via a network of lines 6, 16, 26, 250 and valves 116, 126, 326 forming a parallel connection and a series link between the two heat exchangers 15, 25 and a bypass line 250 (bypass) of the second heat exchanger.

Comme visible à la figure 1, le second échangeur 15 de chaleur est de préférence du type à tube (par exemple en inox, en cuivre ou autre alliage compatible avec les températures cryogéniques) immergé dans un bain de fluide auxiliaire de refroidissement tel que de l'azote liquide à 80K. Plus précisément, le second échangeur de chaleur 15 est immergé dans une première capacité 3 d'azote liquide. Comme décrit précédemment, la première capacité 3 peut être alimentée en fluide auxiliaire via une conduite 113 d'amenée reliée à une source de fluide auxiliaire (non représentée) et munie d'une vanne 23.As visible at figure 1 the second heat exchanger is preferably of the tube type (for example stainless steel, copper or other alloy compatible with cryogenic temperatures) immersed in a bath of auxiliary cooling fluid such as liquid nitrogen at 80K. More specifically, the second heat exchanger 15 is immersed in a first liquid nitrogen capacity 3. As previously described, the first capacitor 3 can be supplied with auxiliary fluid via a supply duct 113 connected to an auxiliary fluid source (not shown) and provided with a valve 23.

Bien entendu l'invention n'est pas limitée à cet exemple de réalisation. Ainsi, par exemple, ce second échangeur 15 de chaleur immergé peut être un échangeur de chaleur en inox ou autre métal ou alliage à plaque soudées, c'est-à-dire un échangeur dont la technologie est connue en anglais sous la dénomination « Plate and Shell ». Ces types d'échangeurs de chaleur constituant le second échangeur 15 de chaleur sont conformés pour supporter sans inconvénient des écarts de températures relativement importants entre les différentes configurations d'utilisation (immergée/non immergée), par exemple des écarts de températures compris entre 60K et 250K.Of course, the invention is not limited to this embodiment. Thus, for example, this second submerged heat exchanger may be a heat exchanger made of stainless steel or other welded plate metal or alloy, that is to say an exchanger whose technology is known in English under the name "Plate and Shell ". These types of heat exchangers constituting the second heat exchanger are designed to withstand, without disadvantage, relatively large temperature differences between the different use configurations (immersed / non-submerged), for example temperature differences between 60 K and 250K.

Le dispositif comporte une première conduite 30 d'évacuation de fluide auxiliaire vaporisé reliant une extrémité supérieure de la première 3 capacité à un système de récupération de fluide auxiliaire déporté via un passage dans le premier 5 échangeur de chaleur. Cette première conduite 30 d'évacuation de fluide auxiliaire vaporisé comprend également une branche 130 de dérivation (by-pass) sélectif du premier 5 échangeur de chaleur via un système de vannes 230, 430.The device comprises a first vaporized auxiliary fluid discharge conduit 30 connecting an upper end of the first capacitor to a remote auxiliary fluid recovery system via a passage in the first heat exchanger. This first vaporized auxiliary fluid discharge conduit 30 also includes a selective bypass branch 130 of the first heat exchanger via a valve system 230, 430.

Le troisième échangeur 25 de chaleur est de préférence un échangeur en aluminium du type à plaque et ailettes. Le troisième échangeur 25 est du type à échange de chaleur sélectif entre l'hélium et l'azote. A cet effet, et comme visible à la figure 2, le dispositif peut comporter une conduite 13 d'alimentation munie d'au moins une vanne (non représentée) reliant (par exemple en boucle) la première capacité 3 au troisième échangeur 25 de chaleur, pour transférer sélectivement des frigories du fluide auxiliaire vers le gaz de travail dans le troisième 25 échangeur de chaleur.The third heat exchanger is preferably a plate-and-fin type aluminum exchanger. The third exchanger 25 is of the type with selective heat exchange between helium and nitrogen. For this purpose, and as visible at figure 2 the device may comprise a feed pipe 13 provided with at least one valve (not shown) connecting (for example in a loop) the first capacitor 3 to the third heat exchanger, for selectively transferring frigories of the auxiliary fluid to the working gas in the third heat exchanger.

La figure 3 illustre une variante de réalisation du premier étage de refroidissement du dispositif. La forme de réalisation de la figure 3 se distingue de celle de la figure 2 uniquement en ce que le troisième échangeur de chaleur 25 est cette fois immergé dans une seconde capacité 33 de fluide auxiliaire (au lieu d'être alimenté en fluide auxiliaire à partir de la première capacité 3 ou à partir d'une source). Comme illustré à la figure 3, cette seconde capacité 33 de fluide peut être un réservoir cryogénique sélectivement alimenté en fluide auxiliaire par une source de fluide auxiliaire. Le troisième échangeur 25 de chaleur est immergé dans ladite seconde capacité 33 pour permettre le cas échéant un échange de frigories entre le gaz de travail et le fluide auxiliaire de la seconde capacité 33.The figure 3 illustrates an alternative embodiment of the first cooling stage of the device. The embodiment of the figure 3 differs from that of the figure 2 only in that the third heat exchanger 25 is this time immersed in a second capacity 33 of auxiliary fluid (instead of being supplied with auxiliary fluid from the first capacity 3 or from a source). As illustrated in figure 3 this second fluid capacity 33 may be a cryogenic tank selectively supplied with auxiliary fluid by a source of auxiliary fluid. The third heat exchanger is immersed in said second capacitor 33 to allow, if appropriate, an exchange of frigories between the working gas and the auxiliary fluid of the second capacitor 33.

La seconde capacité 33 auxiliaire comporte également une seconde conduite 330 d'évacuation de fluide auxiliaire vaporisé reliant une extrémité supérieure de la seconde 30 capacité à un système de récupération de fluide auxiliaire déporté via un passage dans le premier 5 échangeur de chaleur. Par exemple, la seconde conduite 330 d'évacuation se raccorde à la première conduite 30 d'évacuation de fluide auxiliaire, en amont du premier échangeur 5. C'est-à-dire que le fluide auxiliaire vaporisé dans la seconde capacité 33 peut être réparti entre un passage dans le premier échangeur 5 et/ou la ligne 130 de by-pass évitant ce premier 5 échangeur de chaleur.The second auxiliary capacity 33 also includes a second vaporized auxiliary fluid discharge conduit 330 connecting an upper end of the second capacity to a remote auxiliary fluid recovery system via a passage in the first heat exchanger. For example, the second discharge pipe 330 connects to the first auxiliary fluid discharge pipe 30, upstream of the first heat exchanger 5. That is to say that the auxiliary fluid vaporized in the second capacitor 33 can be distributed between a passage in the first exchanger 5 and / or line 130 bypass avoiding this first 5 heat exchanger.

Les figures 4 à 7 illustrent respectivement quatre configurations distinctes pouvant être utilisées lors d'une succession d'un exemple de fonctionnement possible du dispositif.The Figures 4 to 7 respectively illustrate four distinct configurations that can be used during a succession of an example of possible operation of the device.

Dans une première phase de mise en froid d'un utilisateur 10 illustrée à la figure 4, l'hélium sortant de la station 1 de compression est refroidi par échange thermique dans le premier 5 échangeur de chaleur puis l'hélium refroidi est subdivisé en deux flux (vannes 116 et 126 ouvertes). Un premier de ces deux flux est refroidi dans le second 15 échangeur de chaleur puis passe dans le troisième 25 échangeur de chaleur sans échange thermique (vanne 233 fermée). Le deuxième flux ne passe pas dans le second 15 échangeur de chaleur et est mélangé avec le premier flux sortant du second échangeur de chaleur 15 avant de passer dans le troisième 25 échangeur de chaleur.In a first phase of cooling a user 10 illustrated in the figure 4 the helium leaving the compression station 1 is cooled by heat exchange in the first heat exchanger and the cooled helium is divided into two streams (valves 116 and 126 open). A first of these two streams is cooled in the second heat exchanger and then passes into the third heat exchanger without heat exchange (valve 233 closed). The second stream does not pass into the second heat exchanger and is mixed with the first outflow of the second heat exchanger 15 before passing into the third heat exchanger.

Dans cette première phase, la première capacité 3 est alimentée en fluide auxiliaire (azote) et l'azote vaporisé est évacué par la conduite 30 d'évacuation et la branche 130 de by-pass sans céder des frigories au premier échangeur 5 de chaleur (vanne 230 ouverte dans la branche de dérivation 130 et vanne 430 fermée pour le passage dans le premier échangeur 5).In this first phase, the first capacity 3 is supplied with auxiliary fluid (nitrogen) and the vaporized nitrogen is evacuated via the evacuation pipe 30 and the bypass branch 130 without yielding frigories to the first heat exchanger 5 ( valve 230 open in branch branch 130 and valve 430 closed for passage through the first exchanger 5).

Ceci peut correspondre au début d'une opération de mise en froid d'un utilisateur initialement à une température comprise entre 400K et 250K. Durant cette première phase, la température de l'hélium peut être :

  • environ égale à 300K à la sortie du premier 5 échangeur de chaleur,
  • environ égale à 250K à la sortie du troisième 25 échangeur de chaleur.
This may correspond to the beginning of a cold operation of a user initially at a temperature between 400K and 250K. During this first phase, the temperature of the helium can be:
  • about 300K at the outlet of the first 5 heat exchanger,
  • about 250K at the outlet of the third heat exchanger.

Dans une second phase de mise en froid d'un utilisateur 10 illustrée à la figure 5, l'hélium sortant de la station 1 de compression peut être refroidi par échange thermique dans le premier 5 échangeur de chaleur puis dans le second 15 échangeur de chaleur (vanne 116 ouverte et vanne 126 fermée). L'hélium est ensuite scindé en deux flux dont un premier flux est refroidi dans le troisième 25 échangeur de chaleur et un second flux qui transite par la ligne 250 de by-pass (ouverture de la vanne 326 dans la ligne 250 de by-pass).In a second phase of cooling a user 10 illustrated in FIG. figure 5 the helium leaving the compression station 1 can be cooled by heat exchange in the first heat exchanger and then in the second heat exchanger (valve 116 open and valve 126 closed). The helium is then split into two streams of which a first stream is cooled in the third heat exchanger and a second stream which passes through the bypass line 250 (opening of the valve 326 in the bypass line 250 ).

La première 3 et la seconde capacité 33 sont alimentées en fluide auxiliaire via des conduites 113, 133 d'amenée respectives (vannes 213 et 233 correspondantes ouvertes). Les fluides auxiliaires vaporisés dans les capacités 3, 33 peuvent être évacuées sans passer par le premier échangeur 5 de chaleur, c'est-à-dire via la branche 130 de by-pass (vanne 430 fermée et vanne 230 ouverte).The first 3 and the second capacitor 33 are supplied with auxiliary fluid via respective supply lines 113, 133 (corresponding open valves 213 and 233). Auxiliary fluids vaporized in the capacitors 3, 33 can be evacuated without passing through the first heat exchanger 5, that is to say via the branch 130 of bypass (valve 430 closed and valve 230 open).

Ceci peut correspondre à une opération de mise en froid d'un utilisateur initialement à une température comprise entre 250K et 150K. Durant cette seconde phase, la température de l'hélium peut être :

  • environ égale à 145K à la sortie du premier 5 échangeur de chaleur,
  • environ égale à 120K à la sortie du deuxième 15 échangeur de chaleur.
  • environ égale à 80K à la sortie du troisième 25 échangeur de chaleur,
  • environ égale à 120K dans la branche 130 de by-pass et
  • environ égale à 95K après la jonction aval de la branche 130 de by-pass.
This may correspond to a cold operation of a user initially at a temperature between 250K and 150K. During this second phase, the temperature of the helium can be:
  • about 145K at the outlet of the first 5 heat exchanger,
  • about 120K at the outlet of the second heat exchanger.
  • about 80K at the outlet of the third heat exchanger,
  • about equal to 120K in branch 130 of bypass and
  • about 95K after the downstream junction of branch 130 bypass.

Dans une troisième phase de mise en froid d'un utilisateur 10 illustrée à la figure 6, le gaz de travail sortant de la station 1 de compression peut être refroidi en série par échange thermique dans le premier 5 échangeur de chaleur puis dans le second 15 échangeur de chaleur puis dans le troisième 25 échangeur de chaleur (vanne 116 ouverte, vanne 126 fermée). Le fluide auxiliaire vaporisé dans les première 3 et seconde 33 capacités peut être évacué pour partie via le premier 5 échangeur de chaleur et pour partie via la branche 130 de by-pass (vanne 230 et 430 ouvertes).In a third cooling phase of a user 10 illustrated in FIG. figure 6 the working gas leaving the compression station 1 can be cooled in series by heat exchange in the first heat exchanger and then in the second heat exchanger and then in the third heat exchanger (valve 116 open, valve 126 closed). The auxiliary fluid vaporized in the first 3 and second 33 capacities can be discharged partly via the first heat exchanger and partly via the branch 130 bypass (valve 230 and 430 open).

Ceci peut correspondre à une opération de mise en froid d'un utilisateur initialement à une température comprise entre 150K et 95K. Durant cette seconde phase, la température de l'hélium peut être :

  • environ égale à 130K à la sortie du premier 5 échangeur de chaleur,
  • environ égale à 100K à la sortie du deuxième 15 échangeur de chaleur.
  • environ égale à 80K à la sortie du troisième 25 échangeur de chaleur.
This may correspond to a cold operation of a user initially at a temperature between 150K and 95K. During this second phase, the temperature of the helium can be:
  • about 130K at the outlet of the first 5 heat exchanger,
  • about 100K at the outlet of the second heat exchanger.
  • about 80K at the outlet of the third heat exchanger.

Dans une quatrième phase de mise en froid d'un utilisateur 10 illustrée à la figure 7, le gaz de travail sortant de la station 1 de compression peut être refroidi en série par échange thermique dans le premier 5 échangeur de chaleur puis dans le troisième échangeur 25 de chaleur (sans passer par le second échangeur 15 de chaleur: vanne 116 fermée et vanne 126 ouverte). Seule la seconde capacité 33 peut être alimentée en fluide auxiliaire (vanne 213 fermée et vanne 233 ouverte). Le fluide auxiliaire vaporisé dans la seconde 33 capacité peut être évacué pour partie via le premier 5 échangeur de chaleur et pour partie via la branche 130 de by-pass (vanne 230 et 430 ouvertes).In a fourth cooling phase of a user 10 illustrated in FIG. figure 7 the working gas exiting the compression station 1 can be cooled in series by heat exchange in the first heat exchanger and then in the third heat exchanger (without passing through the second heat exchanger: valve 116 closed and valve 126 open). Only the second capacitor 33 may be supplied with auxiliary fluid (valve 213 closed and valve 233 open). The auxiliary fluid vaporized in the second capacity 33 can be discharged partly via the first heat exchanger and partly via the branch 130 bypass (valve 230 and 430 open).

Ceci peut correspondre à une opération de mise en froid d'un utilisateur initialement à une température comprise entre 95K et 80K. Durant cette seconde phase, la température de l'hélium peut être :

  • environ égale à 95K à la sortie du premier 5 échangeur de chaleur,
  • environ égale à 80K à la sortie du troisième 25 échangeur de chaleur.
This may correspond to a cold operation of a user initially at a temperature between 95K and 80K. During this second phase, the temperature of the helium can be:
  • about 95K at the outlet of the first 5 heat exchanger,
  • about 80K at the outlet of the third heat exchanger.

Enfin, lorsque l'utilisateur 10 a atteint la température basse déterminée de fonctionnement dit normal, le dispositif peut assurer un refroidissement continu (maintien en froid à la température déterminée) avec le même dispositif.Finally, when the user 10 has reached the determined low temperature of so-called normal operation, the device can ensure continuous cooling (keeping cold at the determined temperature) with the same device.

Durant ce refroidissement continu, le dispositif peut fonctionner également selon la configuration de la figure 7. C'est-à-dire que le gaz de travail sortant de la station 1 de compression peut être refroidi en série par échange thermique dans le premier 5 échangeur de chaleur puis dans le troisième échangeur 25 de chaleur (sans passer par le second échangeur 15 de chaleur) et seule la seconde capacité 33 peut être alimentée en fluide auxiliaire. Le fluide auxiliaire vaporisé dans la seconde 33 capacité peut être évacué via le premier 5 échangeur de chaleur (vanne 230 fermée et vanne 430 ouvertes).During this continuous cooling, the device can also function according to the configuration of the figure 7 . That is, the working gas exiting the compression station 1 can be cooled in series by heat exchange in the first heat exchanger and then in the third heat exchanger (without passing through the second heat exchanger 15). of heat) and only the second capacitor 33 can be supplied with auxiliary fluid. The auxiliary fluid vaporized in the second capacity can be discharged via the first heat exchanger (valve 230 closed and valve 430 open).

Durant ce mode de fonctionnement, la température de l'hélium peut être :

  • environ égale à 90K à la sortie du premier 5 échangeur de chaleur,
  • environ égale à 80K à la sortie du troisième 25 échangeur de chaleur.
During this operating mode, the temperature of helium can be:
  • about 90K at the outlet of the first 5 heat exchanger,
  • about 80K at the outlet of the third heat exchanger.

Les architectures décrites ci-dessus permettent ainsi de mettre en froid un composant massif d'une température relativement chaude (par exemple 400K à une température relativement basse (par exemple 80K) avec un nombre d'équipements réduit.The architectures described above thus make it possible to cool a massive component of a relatively hot temperature (for example 400K at a relatively low temperature (for example 80K) with a reduced number of equipment.

L'utilisation de deux échangeurs de type en aluminium à plaque et ailettes (premier 5 et troisième 25 échangeur de chaleur) et d'un échangeur de chaleur du type à tube (second échangeur 15) permet d'optimiser le fonctionnement du dispositif pour les phases de fonctionnement différentes que sont le pré-refroidissement et le fonctionnement dit normal (après pré-refroidissement).The use of two plate and fin type aluminum exchangers (first and third heat exchangers) and a tube type heat exchanger (second exchanger 15) makes it possible to optimize the operation of the device for different operating phases such as pre-cooling and so-called normal operation (after pre-cooling).

Ces configurations permettent notamment de disposer le second échangeur de chaleur 15 en dehors de la boîte froide 2 et donc également la première capacité 3.These configurations make it possible in particular to arrange the second heat exchanger 15 outside the cold box 2 and thus also the first capacitor 3.

Un autre avantage procuré par le dispositif est de limiter les entrées de chaleur sur le gaz de travail en opération normal par isolation des circuits et équipements utilisés uniquement pour la mise en froid. Ces équipements peuvent être installés en dehors de la boite froide et cela réduit également la taille et le coût de l'enceinte de la boite froide.Another advantage provided by the device is to limit the heat input to the working gas in normal operation by isolating the circuits and equipment used only for cooling. This equipment can be installed outside the cold box and it also reduces the size and cost of the enclosure of the cold box.

Claims (15)

  1. Device for refrigerating and/or liquefying a working gas containing helium or consisting of pure helium, the device comprising a working circuit in the form of a loop for the working gas and comprising, in series:
    - a working gas compression station (1) provided with at least one compressor (11, 12),
    - a cold box (2) for cooling the working gas, comprising a plurality of heat exchangers (5) positioned in series and at least one member (7) for expanding the working gas,
    - a system (14) for the exchange of heat between the cooled working gas and a user (10),
    - at least one return pipe (9) for returning to the compression station (1) the working gas that has passed through the heat exchange system (14), the return pipe (9) comprising at least one heat exchanger (5) for reheating the working gas, the device further comprising an additional pre-cooling system for pre-cooling the working gas leaving the compression station (1), the pre-cooling system comprising at least one volume (3) of auxiliary cryogenic fluid such as liquid nitrogen, the volume (3) being connected to the working circuit via at least one heat exchanger in order to selectively transfer frigories from the auxiliary fluid to the working gas, the cold box (2) comprising a first working-gas cooling stage comprising a first (5) heat exchanger positioned at the output of the compression station (1) in addition to a second (15) heat exchanger, characterised in that the pre-cooling system comprises a third (25) heat exchanger, the first (5) heat exchanger being of the aluminium plate-fin type, the second heat exchanger (15) being of the tube or welded-plate type, said second heat exchanger (15) being immersed in an auxiliary cooling fluid bath, the second (15) and third (25) heat exchangers being connected both in series and in parallel to the working circuit downstream of the first (5) heat exchanger, i.e. the working gas cooled in the first (5) heat exchanger can be admitted selectively to the second (15) and/or to the third (25) heat exchanger, and in that the second (15) heat exchanger is immersed in the first volume (3) of auxiliary liquefied gas.
  2. Device according to claim 1, characterised in that the second heat exchanger (15) is one of the following group: an aluminium or stainless steel tube heat exchanger, an aluminium or stainless steel finned tube heat exchanger, or a stainless steel welded plate heat exchanger.
  3. Device according to either claim 1 or claim 2, characterised in that the circuit comprises a branch (250) for selectively bypassing the third (25) heat exchanger, selectively allowing the working gas leaving the first (5) and/or the second (15) heat exchanger to avoid the third (25) heat exchanger in the working circuit.
  4. Device according to any one of claims 1 to 3, characterised in that it comprises a first vaporised auxiliary fluid discharge pipe (30) connecting an upper end of the first (3) volume to a remote auxiliary fluid recovery system via a passage in the first (5) heat exchanger.
  5. Device according to claim 4, characterised in that the first vaporised auxiliary fluid discharge pipe (30) comprises a branch (130) for selectively bypassing the first (5) heat exchanger.
  6. Device according to any one of claims 1 to 5, characterised in that the third heat exchanger (25) is of the type allowing for the selective exchange of heat between the working gas and the auxiliary fluid, the device comprising a selective feed pipe (13) connecting the first volume (3) to the third heat exchanger, in order to transfer frigories from the auxiliary fluid to the working gas in the third (25) heat exchanger.
  7. Device according to any one of claims 1 to 6, characterised in that it comprises a second fluid volume (33) selectively supplied with auxiliary fluid by an auxiliary fluid source and in that the third heat exchanger (25) is immersed in said second volume (33) to allow for an exchange of frigories between the working gas and the auxiliary fluid of the second volume (33).
  8. Device according to any one of claims 1 to 7, characterised in that it comprises a second vaporised auxiliary fluid discharge pipe (330) connecting an upper end of the second (30) volume to a remote auxiliary fluid recovery system via a passage in the first (5) heat exchanger.
  9. Device according to claim 8, characterised in that the second vaporised auxiliary fluid discharge pipe (330) comprises a branch (130) for selectively bypassing the first (5) heat exchanger.
  10. Method for cooling a user (10) using a device for refrigerating and/or liquefying a working gas according to any one of claims 1 to 9, wherein the user (10) is cooled via the heat exchange system (14) of said device.
  11. Cooling method according to claim 10, characterised in that the method comprises a step of pre-cooling the user (10) having an initial temperature that lies in the range 250K to 400K, wherein the working gas leaving the compression station (1) is cooled by exchange of heat in the first (5) heat exchanger, then is divided into two flows, a first flow of which is cooled in the second (15) heat exchanger then in the third (25) heat exchanger, and a second flow of which is directly cooled in the third (25) heat exchanger, and in that the vaporised auxiliary fluid in the first volume (3) is discharged without transferring frigories to the first (5) heat exchanger.
  12. Cooling method according to either claim 10 or claim 11, characterised in that the method comprises a step of pre-cooling the user (10) having an initial temperature that lies in the range 250K to 150K, wherein the working gas leaving the compression station (1) is cooled by exchange of heat in the first (5) heat exchanger, then in the second (15) heat exchanger, then is divided into two flows, a first flow of which is cooled in the third (25) heat exchanger and a second flow of which bypasses the third heat exchanger (25), and in that the third heat exchanger (25) is supplied with auxiliary fluid in order to transfer frigories from the auxiliary fluid to the working gas in the third heat exchanger (25), and in that the vaporised auxiliary fluid in the first volume (3) and/or in contact with the third heat exchanger (25) is discharged without transferring frigories to the first (5) heat exchanger.
  13. Method according to claim 10, characterised in that the method comprises a step of pre-cooling the user (10) having an initial temperature that lies in the range 150K to 95K, wherein the working gas leaving the compression station (1) is cooled by exchange of heat in the first (5) heat exchanger, then in the second (15) heat exchanger, then in the third (25) heat exchanger, and in that at least part of the vaporised auxiliary fluid in the first volume (3) and/or in contact with the third heat exchanger (25) is discharged and transfers frigories to the first (5) heat exchanger.
  14. Method according to either claim 10 or claim 13, characterised in that the method comprises a step of pre-cooling the user (10) having an initial temperature that lies in the range 95K to 80K, wherein the working gas leaving the compression station (1) is cooled by exchange of heat in the first (5) heat exchanger, then only in the third (25) heat exchanger, and in that the vaporised auxiliary fluid in contact with the third heat exchanger (25) is discharged and transfers frigories to the first (5) heat exchanger.
  15. Method according to any one of claim 10 or claims 13 to 14, characterised in that after a possible pre-cooling phase, the device cools the user according to a so-called nominal operating mode, in which the working gas leaving the compression station (1) is cooled by exchange of heat in the first (5) heat exchanger, then only in the third (25) heat exchanger, and in that the third heat exchanger (25) is supplied with auxiliary fluid in order to transfer frigories from the auxiliary fluid to the working gas in the third heat exchanger (25), and in that the vaporised auxiliary fluid in contact with the third heat exchanger (25) is discharged and transfers frigories to the first (5) heat exchanger.
EP13803115.8A 2012-12-18 2013-11-08 Refrigeration and/or liquefaction device and method thereof Active EP2936006B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1262186A FR2999693B1 (en) 2012-12-18 2012-12-18 REFRIGERATION AND / OR LIQUEFACTION DEVICE AND CORRESPONDING METHOD
PCT/FR2013/052683 WO2014096585A1 (en) 2012-12-18 2013-11-08 Refrigeration and/or liquefaction device, and associated method

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EP2936006A1 EP2936006A1 (en) 2015-10-28
EP2936006B1 true EP2936006B1 (en) 2017-11-08

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EP13803115.8A Active EP2936006B1 (en) 2012-12-18 2013-11-08 Refrigeration and/or liquefaction device and method thereof

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US (2) US10465981B2 (en)
EP (1) EP2936006B1 (en)
JP (1) JP6495177B2 (en)
KR (1) KR102119918B1 (en)
CN (1) CN104854413B (en)
FR (1) FR2999693B1 (en)
WO (1) WO2014096585A1 (en)

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CN114111415A (en) * 2021-08-31 2022-03-01 江苏科技大学 Ultralow-temperature and high-pressure modular integrated compact high-efficiency heat exchanger and detection method

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CN104854413A (en) 2015-08-19
JP2016503876A (en) 2016-02-08
JP6495177B2 (en) 2019-04-03
US10465981B2 (en) 2019-11-05
US20150316315A1 (en) 2015-11-05
FR2999693B1 (en) 2015-06-19
EP2936006A1 (en) 2015-10-28
KR102119918B1 (en) 2020-06-05
FR2999693A1 (en) 2014-06-20
US20200041201A1 (en) 2020-02-06
WO2014096585A1 (en) 2014-06-26
CN104854413B (en) 2017-02-01
KR20150099523A (en) 2015-08-31

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