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
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
  • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • 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
  • F25B40/00—Subcoolers, desuperheaters or superheaters
• • 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
  • F25B6/00—Compression machines, plants or systems, with several condenser circuits
  • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
• • 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
  • F25J1/0221—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 using the cold stored in an external cryogenic component in an open refrigeration 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
  • 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
  • F25J1/0263—Details of the cold heat exchange system using different types of heat exchangers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D9/0006—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the plate-like or laminated conduits being enclosed within a pressure vessel
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
  • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
  • F28F21/081—Heat exchange elements made from metals or metal alloys
  • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
  • F28F21/083—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys from stainless steel
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
  • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
  • F28F21/081—Heat exchange elements made from metals or metal alloys
  • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
• • 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
  • F25J2270/912—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
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
  • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
  • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F2275/00—Fastening; Joining
  • F28F2275/04—Fastening; Joining by brazing
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F2275/00—Fastening; Joining
  • F28F2275/06—Fastening; Joining by welding

Definitions

• the present invention relates to a refrigeration and / or liquefaction device and a corresponding method.
• It relates more particularly to a refrigeration process using a working gas such as pure helium or a gaseous mixture containing helium.
• cold box which may include expansion turbines and / or a plurality of heat exchangers.
• brazed aluminum heat exchangers should be protected during this transient regime, which can sometimes be extended over a long period of time, and for example to reach a few tens of days in the case of a cryogenic installation for cooling magnets to superconductors.
• cryogenic installations may show unequal performance between the transient and the established regime, being less well suited to one operating regime than to the other.
• cryogenic plants have a large footprint and a complex structure, expensive to set up and maintain.
• the objects assigned to the invention therefore aim at overcoming the aforementioned drawbacks and at proposing a new efficient and versatile refrigeration process which makes it possible to obtain, whatever the operating regime, and by means of a cryogenic installation simple and compact, efficient cooling and respectful of said cryogenic installation.
• the objects assigned to the invention are achieved by means of a refrigeration process in which a user, being at a temperature called “user temperature”, is supplied with frigories by means of a working gas, such as helium, which is cooled in a refrigeration circuit which comprises at least one compression station, in which said working gas is compressed, then at least one cold box in which the working gas is cooled by passing it through through a plurality of heat exchangers, said method comprising a step (a) for cooling, during which a cold phase (a1) is used for the frigories introduced by the gas cooled down to lower the user temperature, while said user temperature is greater than 150K, and / or a step (b) cold keeping, during which the frigories made by the gas are used.
• a working gas such as helium
• the working gas is cooled by circulating said working gas in a cold box which comprises in series at least one first brazed plate and finned aluminum heat exchanger, a second welded plate heat exchanger, and a third brazed plate and finned aluminum heat exchanger, such that at least 1%, and preferably at least 4%, of the flow of said working gas from the compressor station and entering the cold box through the second exchanger, then at least 1%, and preferably at least 4% %, of said flow of working gas through the third exchanger, before directing said flow of working gas to the user to feed the latter in frigories.
• a second intermediate heat exchanger with welded plates, preferably made of stainless steel (or in another suitable alloy, preferably separate from the aluminum), capable of withstanding strong temperature gradients between fluids that exchange heat through it, and forcing at least a portion, if necessary most, if not all, of the working gas stream to go through this second exchanger, is preserved in all circumstances the cold box, including aluminum heat exchangers, thermomechanical stresses.
• the second heat exchanger since the second heat exchanger withstands strong temperature gradients without damage, it can handle alone a cooling of the working gas of high amplitude (typically of amplitude greater than or equal to 100K, 150 K or 200K) representing a large part, if not (largely) majority, of the desired lowering of the temperature of the working gas.
• high amplitude typically of amplitude greater than or equal to 100K, 150 K or 200K
• the second exchanger By “absorbing" itself the greater part of the temperature difference to be treated to suitably cool the working gas, the second exchanger does not leave the load of the other exchangers (first exchanger and, especially, third exchanger), more efficient but more fragile, than a small residual cooling amplitude (typically less than or equal to 50 K, or even less than or equal to 30 K), significantly lower than that treated by said second exchanger.
• the residual cooling amplitude allocated to each of the first and third heat exchangers thus never exceeds the temperature gradient tolerated by the exchanger concerned.
• the second heat exchanger thus effectively protecting the first and third heat exchanger against thermal "overloads", the longevity and performance of the latter are increased.
• the method is particularly suitable for cooling a relatively "hot” user, whose initial temperature exceeds 150 K at the moment when the cooling process according to the invention is implemented.
• This performance is particularly advantageous in steady state, during the step (b) of maintaining cold, when said method is implemented to maintain the state of a "cold" user (whose user temperature is typically less than 95 K, and for example of the order of 80 K).
• the fact of maintaining, in the steady state of maintaining the cold, at least partial, or even total circulation, of the flow of working gas through the second exchanger (with welded plates), in addition to the final circulation in the third exchanger (brazed aluminum), allows a portion of the cooling by the second exchanger, upstream of the third exchanger, so that it is possible to use a third exchanger less bulky than before.
• the process according to the invention proves to be particularly versatile, since it makes it possible to efficiently manage, and by means of a particularly simple and compact cold box structure, all the life situations of the cryogenic installation, since the cooling down of the user until the low temperature of said user is maintained (and, where appropriate, until the and when the user returns to ambient temperature at the end of the cooling cycle).
• the process according to the invention therefore advantageously makes it possible to combine the advantages of aluminum exchangers in terms of thermal performance, particularly at very low temperatures, with the thermo-mechanical strength of the intermediate heat exchanger with welded plates.
• FIG. 1 represents, in a schematic view, the implementation of a refrigeration method according to the invention.
• the present invention relates to a refrigeration process, during which a user 1, at a temperature called “user temperature” T1, is fed in frigories by means of a working gas, such as helium, which is cooled in a refrigeration circuit 2.
• a working gas such as helium
• User 1 can be an industrial installation of any kind, requiring a supply of frigories.
• the method will be used to supply cold superconducting cables, for example within electromagnets for confining a plasma.
• the process may be, if appropriate, a process for liquefying a gas, and in particular a process for liquefying nitrogen or any other gas, for example helium.
• the working gas may especially be pure helium or a gaseous mixture containing helium.
• circulating said working gas will be circulated in a refrigeration circuit 2 closed to recycle said working gas, and thus subject it continuously to these repeated cycles of compression / cooling, and optionally expansion.
• the invention also relates of course to a refrigeration circuit 2, and more generally to a cryogenic installation allowing the implementation of such a method.
• the refrigeration circuit 2 comprises at least one compression station 3, in which said working gas is compressed, and then at least one cold box 4 ("cold box ") In which the working gas is cooled by passing it through a plurality of heat exchangers 5, 15, 25, in this case a first exchanger 5, a second exchanger 15, and a third exchanger 25.
• said cold box may also comprise at least one expansion turbine (not shown) intended to cool the working gas by subjecting it to adiabatic or quasi-adiabatic expansion.
• the refrigeration circuit 2 feeds user 1 into fridges via a suitable heat exchange system 6 connected downstream of the third exchanger 25.
• the cold box 4 may comprise two identical refrigeration circuits 2 operating in parallel, that is to say each receiving part of the flow of working gas from the compression station 3 and cooling each the portion of working gas that is allocated to them before directing said working gas to the user 1 at the outlet of the cold box.
• the method comprises a step (a) of cooling ("cool down"), during which one uses, during a first phase (a1) of cooling, the frigories brought by the working gas cooled to lower the user temperature T1, while said user temperature T1 is greater than 1 50K, and / or alternatively or complementary to said step (a) cooling, a step (b) of maintenance in cold ("normal operation"), during which the frigories made by the cooled working gas are used, while the user temperature T1 is below a set point of cold, less than 95 K, so maintain the user temperature T1 under said cold setpoint.
• the working gas is cooled by circulating said working gas in a cold box 4 which comprises in series at least one first brazed plate and finned aluminum heat exchanger 5, a second welded plate heat exchanger, and a third aluminum heat exchanger 25 with brazed plates and fins, such that at least 1%, and preferably at least 4%, of the flow of said working gas, which comes from the compression station 3 and which enters the box, is passed through cold (4), through the second exchanger 15, then thereafter at least 1%, and preferably at least 4%, of said working gas stream through the third exchanger 25, before directing said working gas flow, and more particularly the entire flow of gas passed through the cold box 4, to the user 1 to supply the latter with frigories.
• the minimum amount of working gas passing through the second exchanger 15, and or the third exchanger 25, may especially be between 4% and 5%, and for example of the order
• the flow of the working gas and the proportions of said gas flow expressed in percentages, correspond to the mass flow rate of the working gas (refrigerant), and respectively to percentages of said mass flow rate.
• the second exchanger 15 By providing for a systematic traversing, at each work cycle, of at least a part (not zero), or even a majority, of the working gas on the one hand through the second exchanger 15 with welded plates, particularly resistant to high temperature gradients, and secondly through the third heat exchanger 25 aluminum plates and fins, particularly thermally efficient at low temperatures, it manages to effectively manage refrigeration as well during transients, especially during the first phase (a1) for cooling a "warm” or "hot” user (whose temperature T1 initially exceeds 150K), the second exchanger 15 then supporting most of the thermal shock, that during the steady state of maintenance cold, during which the third exchanger 25 then plays a leading role.
• the flow pattern of the working gas is preferably such that, during step (a) cooling, and more particularly its first phase (a1), or during the step (b) of maintenance in during all these stages, the majority is controlled, that is to say more than 50%, preferably more than 75%, more than 80% or even more than 90%, or even preferably, the totality, 100%, of the working gas that enters the cold box 4, and if necessary, more generally, the working gas that comes out, at "high pressure" (in practice about 18 bar), from the compression station 3, to the first exchanger 5, so that the majority or all of the flow of said working gas that enters the cold box 4 actually passes through said first exchanger 5 to to be cooled.
• "high pressure" in practice about 18 bar
• step (b) of keeping cold it is preferable to pass the majority, and preferably all, of the flow of working gas that enters into the cold box 4 first through the first heat exchanger 5, before passing all or part of said flow of working gas through the second heat exchanger 15 then all or part of said flow of working gas through the third exchanger 25.
• the fact of simultaneously exploiting, at least part of their processing capacity, the three heat exchangers 5, 15, 25 present in the cold box, and what is in cold-start situation or of maintenance in cold improves the overall efficiency of the cold box 4 while limiting the individual size of each exchanger 5, 15, 25, and therefore the overall size of said cold box 4.
• the entire flow working gas passing through the second exchanger 15 then also passes through the third exchanger 25.
• the step (a) of cooling, and more particularly the first phase (a1) of cooling is implemented while the initial user temperature T1 is greater than or equal to 200 K, 250 K at 300 K or 350 K.
• the process, and more particularly the first phase (a1) of step (a) of cooling will be implemented to feed a (or) users whose temperature T1 will not exceed 450 K, and preferably 400 K.
• the first phase (a1) of the stage (a) of cooling can be implemented while, or even as long as, the user temperature T1 is between 150 K (strictly) and 400 K, and more particularly between 150 K (strictly) and 350 K, for example between 250 K and 350 K, or even between 250 K and 300 K.
• the permanent circulation of the working gas through the second exchanger 15 ensures in fact at all times a protection of the cold box 4 against the effects of large temperature differences, which gives great versatility to the process, which can take directly in charge of both "cold” users (whose temperature T1 is less than 95K, and especially between 70K and (strictly) 95K) that "hot” users (typically at temperature T1 higher (strictly) to 150 K, and especially at room temperature close to 300K), or even “very hot” users (whose T1 temperature can for example reach 350K or 400K).
• the majority, or even the totality of the flow of working gas then passes through the third exchanger 25, located downstream of the second exchanger 15, so as to yield (a third time) to the heat and thus continue cooling.
• the working gas flow from the second heat exchanger 15 will preferably be completely collected at the outlet of said second heat exchanger 15 and conveyed as a whole through the third heat exchanger 25, during this same step (b) keeping cold.
• the entire flow of working gas from the compression station 3 can be sent to the first exchanger 5, then to the second exchanger 15, then to the third exchanger 25, so that the entire flow of working gas successively pass through the first exchanger 5, then the second exchanger 15, then the third exchanger 25 during a single cycle working (that is to say during the same "tower" refrigeration circuit 2), before feeding the user 1, then return to the compressor station 3.
• the cold-forming step (a) continues, after the first cooling phase (a1), with a second cooling phase (a2) during which the cooling initiated during the cooling is prolonged. the first phase (a1) of cooling until the user temperature (T1) reaches the cold set point.
• the cold keeping step (b) is then preferably engaged while maintaining a circulation of the working gas through the second heat exchanger 15.
• step (a) of cooling it is conceivable to maintain, during the transition from step (a) of cooling to step (b) of maintaining cold, a distribution configuration of the flow of working gas through the first, second and third heat exchangers 5, 15, 25 which is substantially identical to the distribution pattern which was used in the cold-forming step (a).
• the material connections between the first, second and third exchangers 5, 15, 25 within the cold box 4, and therefore the layout of the refrigeration circuit 2 taken by the working gas, can then remain unchanged. under any circumstances, whatever the operating mode of said cold box 4.
• This permanence makes it possible to simplify the arrangement and management of said cold box 4, and thus to reduce not only the bulk, but also the cost and operating cost, while improving its reliability and longevity.
• step (a) of cooling and more particularly during the first phase (a1) of cooling, the flow of working gas is distributed upstream of the second exchanger 15, between a first branch 8, called “cooling branch”, shown in solid lines in FIG. 1, which passes successively through the second exchanger 15 and the third exchanger 25, and a second branch 9, said "bypass branch”, shown in dotted line in Figure 1, which bypasses the second exchanger 15 and the third exchanger 25 to then join the flow of working gas from said third exchanger 25.
• the bypass branch 9 makes it possible to achieve a "by-pass" of the entire cooling branch 8, by conveying a portion of the working gas directly from a sampling point provided with a flow distributor 10 and located downstream of the first exchanger 5 and upstream of the second exchanger 15, to a junction point 1 1 located downstream of the third exchanger 25 and upstream of the user 1 (without intersecting, in particular, the cooling branch 8 between the second and third exchangers 15, 25).
• the second heat exchanger 15 and especially the third heat exchanger 25 is less stressed during the step (a) of setting in cold, which in particular makes it possible to limit the thermal stresses as well as the losses of load.
• the adaptation of the refrigeration circuit 2 to the operating regime considered at a given moment may be operated by a simple adjustment of the working gas flow rate and / or the flow rate of the cold auxiliary fluids through the first, second and third exchangers 5, 15, 25.
• the first heat exchanger 5 and the third heat exchanger 25 are advantageously of the type aluminum exchangers with brazed plates and fins ("aluminum flat-ends heat exchanger"), and may as such be in accordance with the recommendations of ALPEMA ("Aluminum Plate- Heat Exchanger Manufacturer's Association "Association of Brazed Aluminum Plate and Wave Heat Exchanger Manufacturers).
• Such aluminum heat exchangers are indeed both particularly compact and thermally efficient.
• a second exchanger 15 is a stainless steel welded plate heat exchanger or, where appropriate, a suitable stainless metal alloy other than aluminum (which is too fragile).
• Such an exchanger the technology of which is also known by the name “plate and shell”, and which naturally has a number of plates (typically more than three plates) and an exchange surface adapted to the application, indeed presents a great robustness, and in particular an excellent mechanical resistance to strong thermal gradients.
• a second exchanger 15 is a printed circuit heat exchanger ("PCHE", for "Printed Circuit Heat Exchanger”).
• Such an exchanger formed by the assembly (for example by welding in the oven) of a plurality of stacked plates in which grooves, forming the circulation channels, have been previously etched by etching, is in advantageously particularly compact effect.
• the second exchanger 15 may form a countercurrent exchanger, as illustrated in FIG. 1, in which the working gas, in this case helium (He), circulates at countercurrent of a cold fluid to give heat to the latter, which then evacuated by means of a suitable device.
• the working gas in this case helium (He)
• He helium
• a relatively hot working gas for example up to 270K or 300K at the inlet of the exchanger 15.
• a particularly cold auxiliary fluid such as liquid nitrogen, having an inlet temperature of the order of 80.8K
• a cold auxiliary fluid such as liquid nitrogen (“LIN”), preferably against the current, to cool the working gas.
• LIN liquid nitrogen
• the second heat exchanger 15 can thus form a liquid helium-nitrogen type circuit-type exchanger ("HE-LIN PCHE"), within which liquid nitrogen (“LIN”), circulating in the countercurrent of the working gas (“He”), and typically having an inlet temperature of the order of 80.8K, vaporizes to nitrogen gas (“N2”) to withdraw calories to said working gas (“He”).
• HE-LIN PCHE liquid helium-nitrogen type circuit-type exchanger
• the first heat exchanger 5 used is a gas / gas exchanger, preferably against the current, in which the return working gas of the user 1 receives, before joining the inlet of the compression station 3, the heat given off by the compressed working gas coming from said compression station 3.
• the return pipe 7 can thus pass through the first exchanger 5, of the brazed aluminum helium-helium exchanger type ("BAHX He-He", for "Brazed Aluminum Heat eXchange He-He ") so that the helium” cold “(typically about 100K) and” low “pressure (typically 16 bar) that goes back to the compression station 3 can heat up (typically, go to temperature ambient, are between 290K and 307K approximately) while circulating against the Helium compressed (typically about 18 bar) and "hot” (typically around 300K to 310K) coming out of the compression station 3 to go down to the user 1.
• BAHX He-He brazed Aluminum helium-helium exchanger type
• thermosiphon preferably cocurrent.
• auxiliary fluid constituted by liquid nitrogen (LIN) at the co-current of the helium flow (working gas) which descends towards the user 1 .
• Nitrogen which typically passes from 79.8K to 80.8K in said third exchanger 25, and which changes from the liquid state (“LIN”) to the gaseous state ("GAN", for "Gaseous Nitrogen") , captures the heat of the Helium flow, and thus lowers the temperature of it to about 80K.
• the user temperature T1 may be of the order of 300 K (ambient temperature).
• the temperature of the working gas which rises towards the compression station 3 and which enters the first exchanger as a cold fluid is then of the order of 300 K.
• the rising gas captures heat through the first exchanger 1, and can thus be found at about 307K, and at low pressure of the order of 16 bar, at the input of the compression station 3.
• the high pressure gas approximately 18 bar, has a temperature of 310K when it reaches the first exchanger 5.
• the second exchanger 15 which supports most of the cooling, perfectly tolerates countercurrent circulation on the one hand of helium (working gas) which goes from 302K to 95K, and on the other hand liquid nitrogen (auxiliary fluid) which has a very low temperature, of the order of 80 K, and which changes from the liquid state to a gaseous state or diphasic liquid / gas.
• working gas which goes from 302K to 95K
• auxiliary fluid which has a very low temperature, of the order of 80 K, and which changes from the liquid state to a gaseous state or diphasic liquid / gas.
• This flow at 80K coming out of the third heat exchanger 25 then mixes, at a junction point denoted 1 1 in FIG. 1, with the flow at 302K coming from the bypass branch 9, then the whole of the working gas comes to feed the exchange system 6 of the user 1.
• the working gas In steady state, that is to say during the step (b) of maintaining cold, and more preferably while the working gas circulates exclusively in the cooling branch 8, the working gas typically has a temperature of the order of 103K at the input of the second exchanger 15, and about 95K at the output of said second exchanger 15, which is therefore significantly less stressed than transient.
• the working gas that reaches the user can then advantageously have a very low temperature, of the order of 80.4K.
• the first heat exchanger 5 (BAHX He-He) is traversed by the entire gas flow of work (here helium) that enters the cold box 4, and this, moreover, both when one is in transient cold mode, than when one is in steady state maintenance mode. cold.
• the entire flow of working gas passes through said first exchanger 5 a first time, as a hot fluid to be cooled, entering the cold box 4 to be cooled, then a second time, as a cold fluid, returning from the user 1, before emerging from said cold box 4.
• the invention also relates as such to a refrigeration device arranged to implement a refrigeration method according to one or other of the above characteristics.
• It relates more particularly to a cold box 4 allowing the implementation of said method, and more particularly arranged to ensure a circulation of the working gas according to the invention.
• the invention thus relates more particularly to a cold box 4 intended for the cooling of a working gas, said cold box comprising in series, in a same heat-insulated enclosure, at least a first aluminum heat exchanger 5 with brazed plates and fins, a second welded plate stainless steel heat exchanger; and a third aluminum heat exchanger with brazed plates and fins.
• said cold box comprises at least a first working gas circulation branch 8, called “cooling branch” 8, which passes successively through the second exchanger 15 and the third exchanger 25, and a second branch 9 working gas flow, called “bypass branch” 9, which bypasses the second exchanger 15 and the third exchanger 25 to join, preferably directly, the output of the third exchanger 25, and a flow distributor 10 arranged to selectively direct the flow of working gas from the first exchanger 5 exclusively into the first branch 8 called "cooling", or to distribute said flow of working gas partly in the first branch 8, called “cooling” and for part in the second branch 9, called “derivation".
• the flow splitter 10 may take the form of a multi-way valve or a feeder provided with an inlet, connected to the outlet of the first exchanger 5, and at least two outlets, one of which connected to the first branch 8, and the other to the second branch 9, at least one of said outputs, and preferably each of said outputs, being provided with at least one valve allowing, if necessary to adjust the flow rate of working gas in branch 8, 9 corresponding.
• bypass branch 9 will not communicate with the pipe which joins the outlet of the second heat exchanger 1 5 to the inlet of the third heat exchanger 25, so that all of the working gas taken upstream of the second heat exchanger 15 by the said branch branch 9 will be directly conveyed by it to a junction point 1 1 located downstream of the third exchanger 25, and upstream of the user 1, junction point 1 1 where said gas will be mixed with the gas flow from said third exchanger 25.
• Such a cold box variant 4 advantageously allows a simple and fast switching between a preferred configuration of transient regime (in particular cooling), in which the branch branch 9 is active, so that the flow of gas passing through the box 4, and from the first exchanger 5, is distributed between the cooling branch 8 (at least 1%, and preferably at least 4%) on the one hand, and the branch branch 9 d on the other hand, and a preferred steady-state configuration (cold hold), in which the flow splitter 10 reduces or even closes the access to the branch branch 9, so that a proportion of the gas flow of greater work than that concerned during the transient regime, and preferably the majority or all of the said flow of working gas through the second exchanger 15 and the third exchanger 25.
• a preferred configuration of transient regime in particular cooling
• the branch branch 9 is active, so that the flow of gas passing through the box 4, and from the first exchanger 5 is distributed between the cooling branch 8 (at least 1%, and preferably at least 4%) on the one hand, and the branch branch 9 d on the other hand
• said exchangers 5, 15, 25 may be connected in series with each other in this order so as to form a linear cooling circuit (whose path typically corresponds to the cooling branch 8 mentioned in the foregoing), intended for the passage of the working gas, said circuit being physically devoid of branches or branch branches which would be able to allow the working gas to bypass one either of the said heat exchangers 5, 15, 25, in such a way that the entire flow of working gas passing through the first heat exchanger 5 then necessarily and successively passes through the second heat exchanger 15 and then the third heat exchanger 25 by passing through said cooling circuit .
• the cold box 4 is thermally insulated from its environment by pearlite.
• the invention also relates to a cryogenic installation as such, allowing the implementation of a refrigeration method according to the invention.
• Said installation may for this purpose include a control module and configuration of the cold box 4, said module controlling the exchanger circuit 5, 15, 25 of said cold box so as to leave permanently access to the second heat exchanger 15 and at the third exchanger 25, in order to permanently direct at least 1%, preferably at least 4%, of the flow of working gas entering the cold box 4 through the second exchanger 15 and through the third exchanger 25.
• the invention relates in particular to a cryogenic plant comprising a loop refrigeration circuit 2 for a working gas, said refrigeration circuit 2 comprising in series at least one compression station 3, intended to compress said working gas, then to least one cold box 4 according to one or other of the above-mentioned variants, said cold box 4 being intended for cooling the working gas by passing it through a plurality of heat exchangers 5, 15, 25, then a heat exchange system arranged to allow the cooled working gas from the cold box 4 to yield a user 1.
• the invention is not limited to the only variants described, the person skilled in the art being able to isolate or combine freely between them one or the other of the aforementioned characteristics or to substitute them equivalents.
• the considerations related to the transient cooling regime may apply mutatis mutandis to the warming of the user, that is to say to the progressive return of the user from a cold state to a hot state, at the end of the cooling cycle.

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• 2013
  • 2013-12-06 FR FR1362240A patent/FR3014544A1/fr active Pending
• 2014
  • 2014-11-06 JP JP2016536550A patent/JP6495284B2/ja active Active
  • 2014-11-06 WO PCT/FR2014/052837 patent/WO2015082788A1/fr active Application Filing
  • 2014-11-06 EP EP14806019.7A patent/EP3077736B1/de active Active
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