EP3465030B1 - Dispositif cryogenique a echangeur compact - Google Patents

Dispositif cryogenique a echangeur compact Download PDF

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Publication number
EP3465030B1
EP3465030B1 EP17735183.0A EP17735183A EP3465030B1 EP 3465030 B1 EP3465030 B1 EP 3465030B1 EP 17735183 A EP17735183 A EP 17735183A EP 3465030 B1 EP3465030 B1 EP 3465030B1
Authority
EP
European Patent Office
Prior art keywords
pellets
capillary
generation device
cold generation
mandrel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17735183.0A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3465030A1 (fr
Inventor
Jean-Christophe TERME
Ahmad Sultan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Lynred SAS
Original Assignee
Lynred SAS
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Priority to SI201730180T priority Critical patent/SI3465030T1/sl
Publication of EP3465030A1 publication Critical patent/EP3465030A1/fr
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Publication of EP3465030B1 publication Critical patent/EP3465030B1/fr
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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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • 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
    • F25B9/02—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/003—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by using permeable mass, perforated or porous materials
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/02—Gas cycle refrigeration machines using the Joule-Thompson effect
    • F25B2309/022—Gas cycle refrigeration machines using the Joule-Thompson effect characterised by the expansion element
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/062—Capillary expansion valves
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange

Definitions

  • the invention lies in the general field of cold machines, and more particularly in cold generation devices intended to allow the operation of certain types of detectors, and more particularly infrared detectors of the cooled type, also called detectors. quantum infrared.
  • cryogenic machines In the particular context of infrared detectors, it is desired, for an obvious reason of space, to limit the volume of the cryogenic source. In fact, miniature cryogenic machines frequently use the “Joule-Thomson” expansion principle, thus making it possible to have significant cryogenic power, and therefore rapid cooling, in particular of infrared detectors or electronic compounds. requiring their operation to operate at particularly low temperatures.
  • the devices of the prior art use a Hampson type counter-current exchanger, in which the high pressure fluid circulates in a capillary surrounding a cylindrical sleeve or mandrel, closed by an insulating foam. The heat exchange takes place at the periphery of the sleeve, at the level of which the low pressure fluid circulates against the current.
  • the document FR 2 477 406 A1 discloses a cold generating device according to the preamble of claim 1.
  • the invention relates to a device of the type in question making it possible at the same time to increase the efficiency of such a device, in particular by reducing the TMF, that is to say the time for the installation to cool down. , without altering the size of existing devices or on the contrary, at constant TMF, reducing the size of such devices.
  • the invention proposes a device for generating cold implementing the principle of "Joule-Thomson" expansion, comprising a heat exchanger within which a fluid under high pressure and under low pressure circulates.
  • the heat exchanger consists of the stack of pellets made of porous material, and in particular sintered, constituting a cylindrical mandrel, in contact with which is wound a capillary within which circulates the high pressure fluid, the low fluid pressure circulating against the current inside the porous mandrel thus formed.
  • a porous thermal insulating fabric typically made of glass fibers.
  • the invention basically consists in replacing the mandrel and the fins of the prior art by a stack of sintered and porous material, promoting the thermal exchange of the low pressure fluid with the high pressure fluid circulating in the capillary. peripheral in contact with said material.
  • This optimization of the exchange results from the nature of the material constituting the mandrel, and also makes it possible to dispense with the fins optimizing the heat exchange of the prior art, and consequently, makes it possible to optimize the concentration of turns of the capillary within which the high pressure fluid circulates, and consequently optimizes the compactness of the cold generating device.
  • the pellets are made based on silver sinter or copper sinter.
  • the capillary is made of metal, typically copper, stainless steel, or even a cupronickel alloy.
  • FIG. 1 the operating diagram of a device implementing the “Joule-Thomson” expansion.
  • This diagram shows the source of HP high pressure fluid, this fluid can be a typically argon, nitrogen or air gas, and the return of said fluid after expansion.
  • the double coil (1) shows the countercurrent heat exchanger between the high pressure fluid emanating from the high pressure source HP, and the low pressure fluid, after expansion at the evaporator (2), an expansion valve (3) being mounted before the evaporator.
  • the assembly is integrated within a vacuum enclosure (4).
  • the porosity of these pellets is close to 100 nanometers.
  • the orifices generated by the sintering of the pellets have a typical diameter of 100 nanometers.
  • pads (5) of generally cylindrical shape, are for example assembled to each other by means of fixing rods (6), emanating from the high pressure connector (7), and provided with nuts (8) at their lower base. .
  • the pellets can be glued together.
  • these pellets (5) are separated from each other by an interlayer or grid (9), made of a non-conductive porous material, typically made of a woven fiberglass.
  • interlayer or grid (9) made of a non-conductive porous material, typically made of a woven fiberglass.
  • These spacers have a typical thickness of 0.3 millimeters. The implementation of such spacers tends to oppose any axial thermal conduction, optimizing the heat exchange surface between the two flows, respectively low pressure and high pressure.
  • the assembly thus formed by the pellets and the spacers constitutes a cylindrical mandrel, in contact with which a capillary (10) is wound, within which the high pressure fluid circulates.
  • This capillary is for example made of copper, stainless steel or a cupro-nickel alloy. It typically has an external diameter of 0.5 millimeter and an internal diameter of 0.3 millimeter.
  • the low pressure fluid passes through them and cools them.
  • the pellets cool the high pressure fluid which circulates in the capillary. In fact, good thermal contact is necessary between the capillary and the pellets.
  • the pellets (5) are produced using a mold shaped as a function of the desired shape of said pellets.
  • the silver powder is poured into the mold, and the temperature of the mold is raised to a temperature below the silver melting temperature, in order to obtain a simple sintering without causing the powder to melt.
  • the pellets After the pellets have been produced, they are stacked by inserting the thermal insulating elements (9), the latter having an external diameter less than or equal to that of the pellets (5), so that they cannot come into contact with the capillary (10).
  • the capillary for example made of cupro-nickel alloy undergoes a treatment consisting of a deposit of silver, for example by electrolysis, if the pellets are made of silver sinter.
  • the purpose of this deposit is to promote subsequent contact with the pellets (5), in particular when the capillary is fixed by welding or by soldering.
  • the assembly is placed in an oven to generate the phenomenon of brazing.
  • thermal conductive binder for example consisting of a film of “solgel” type adhesive loaded with metal powder, brushed in the capillary / tablet area.
  • the device of the invention is intended to be integrated into a cylindrical well of a cryostat, as illustrated within the figure 4 .
  • a cryostat (11) is traditionally maintained under vacuum. It receives within the enclosure that it defines an infrared detector (12), positioned directly above a window (13) transparent to the radiation to be detected. Finally, it comprises two wells (14), into which are inserted in each of them a device according to the invention, in order to generate the cold necessary for the operation of said detector.
  • a wire (15) made of insulating material for example made of glass fibers or polyester fibers such as as marketed under the registered trademark terylene®, coming to bear between two consecutive turns of the capillary (10), that is to say in the interval separating said turns, and against the internal wall (16) of the cylindrical well (14 ).
  • the wire (15) is thus wound along the mandrel, then fixed at its two ends, typically by gluing.
  • the consecutive turns of the capillary (10) are therefore thermally insulated from each other.
  • the turns of the capillary (10) are thermally insulated from the well (14).
  • the presence of the wire (15) provides a seal for the device with respect to said well, forcing the low pressure fluid to pass through the pellets (5), and therefore contributing to optimizing the yield of the device of the invention.
  • the operating temperature of the latter is typically between 77K and 250K.
  • the pressure of the high pressure fluid is typically between a few tens to a few hundred bars.
  • the device according to the invention makes it possible to considerably increase the heat exchange surface in comparison with the devices of the prior art, of the type comprising a capillary with fins, typically 1000 times with constant congestion. It is therefore easily understood that the efficiency of such a cold machine is itself increased, or that the size of such a cold machine can be significantly reduced, while retaining the same performance as the devices of the invention. prior art. These results are particularly appreciable in the context of cooled infrared detectors.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Dispersion Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
EP17735183.0A 2016-06-06 2017-06-02 Dispositif cryogenique a echangeur compact Active EP3465030B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
SI201730180T SI3465030T1 (sl) 2016-06-06 2017-06-02 Kriogena naprava s kompaktnim izmenjevalcem

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1655128A FR3052245B1 (fr) 2016-06-06 2016-06-06 Dispositif cryogenique a echangeur compact
PCT/FR2017/051390 WO2017212148A1 (fr) 2016-06-06 2017-06-02 Dispositif cryogenique a echangeur compact

Publications (2)

Publication Number Publication Date
EP3465030A1 EP3465030A1 (fr) 2019-04-10
EP3465030B1 true EP3465030B1 (fr) 2020-01-29

Family

ID=57233543

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17735183.0A Active EP3465030B1 (fr) 2016-06-06 2017-06-02 Dispositif cryogenique a echangeur compact

Country Status (8)

Country Link
US (1) US20190120529A1 (ko)
EP (1) EP3465030B1 (ko)
KR (1) KR102260700B1 (ko)
CN (1) CN109073293B (ko)
FR (1) FR3052245B1 (ko)
IL (1) IL262395B (ko)
SI (1) SI3465030T1 (ko)
WO (1) WO2017212148A1 (ko)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111912132A (zh) * 2020-06-05 2020-11-10 中国空间技术研究院 焦耳-汤姆逊制冷器件及其制备方法
CN114087810B (zh) * 2021-11-16 2022-08-05 西安交通大学 一种节流制冷器
CN114754507A (zh) * 2022-03-11 2022-07-15 上海铂钺制冷科技有限公司 极低温区制冷机用复合型低温负压间壁式换热器

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB945223A (en) * 1961-09-22 1963-12-23 Atomic Energy Authority Uk Improvements in or relating to refrigerators
FR2477406A1 (fr) * 1980-03-06 1981-09-11 Commissariat Energie Atomique Cryosonde chirurgicale
SU903667A1 (ru) * 1980-05-12 1982-02-07 Предприятие П/Я М-5727 Микрохолодильник
JPH0684852B2 (ja) * 1986-01-20 1994-10-26 株式会社東芝 極低温冷凍機
US4781033A (en) * 1987-07-16 1988-11-01 Apd Cryogenics Heat exchanger for a fast cooldown cryostat
JP3674791B2 (ja) * 1994-07-14 2005-07-20 アイシン精機株式会社 冷却装置
US20010030040A1 (en) * 1999-12-23 2001-10-18 Jia Hua Xiao Miniature cryogenic heat exchanger
CN1300521C (zh) * 2002-03-22 2007-02-14 住友重机械工业株式会社 极低温蓄冷器以及冷冻机
US7160291B2 (en) * 2003-06-25 2007-01-09 Endocare, Inc. Detachable cryosurgical probe
JP2005342280A (ja) * 2004-06-04 2005-12-15 Mie Kagaku Kogyo Kk 保温袋体
BR112012004757A2 (pt) * 2009-09-02 2018-03-13 Invensor Gmbh alimentação e distribuição superficial de um refrigerante para um trocador de calor em máquinas de sorção.
CN103423911B (zh) * 2012-06-25 2015-10-28 上海理工大学 制冷器
CN103615823B (zh) * 2013-12-09 2015-11-25 武汉高芯科技有限公司 一种可快速制冷的斯特林-节流复合型制冷机
US20170146268A1 (en) * 2015-11-24 2017-05-25 General Electric Company Water Chiller Apparatus

Also Published As

Publication number Publication date
KR20190015202A (ko) 2019-02-13
KR102260700B1 (ko) 2021-06-03
FR3052245A1 (fr) 2017-12-08
EP3465030A1 (fr) 2019-04-10
US20190120529A1 (en) 2019-04-25
FR3052245B1 (fr) 2019-06-14
CN109073293B (zh) 2020-07-03
WO2017212148A1 (fr) 2017-12-14
IL262395A (en) 2018-12-31
IL262395B (en) 2020-10-29
SI3465030T1 (sl) 2020-03-31
CN109073293A (zh) 2018-12-21

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