EP1469261B1 - Helium- Kühlanlage und zugehöriges Betriebsverfahren - Google Patents

Helium- Kühlanlage und zugehöriges Betriebsverfahren Download PDF

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Publication number
EP1469261B1
EP1469261B1 EP03076111A EP03076111A EP1469261B1 EP 1469261 B1 EP1469261 B1 EP 1469261B1 EP 03076111 A EP03076111 A EP 03076111A EP 03076111 A EP03076111 A EP 03076111A EP 1469261 B1 EP1469261 B1 EP 1469261B1
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EP
European Patent Office
Prior art keywords
cooling system
heat exchanger
regenerator
helium
heat
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.)
Expired - Lifetime
Application number
EP03076111A
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English (en)
French (fr)
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EP1469261A1 (de
Inventor
Alain Ravex
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.)
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Air Liquide SA, LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude filed Critical Air Liquide SA
Priority to DE60325333T priority Critical patent/DE60325333D1/de
Priority to AT03076111T priority patent/ATE418049T1/de
Priority to EP03076111A priority patent/EP1469261B1/de
Publication of EP1469261A1 publication Critical patent/EP1469261A1/de
Application granted granted Critical
Publication of EP1469261B1 publication Critical patent/EP1469261B1/de
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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
    • F25B9/145—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 pulse-tube 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
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F28F3/086—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning having one or more openings therein forming tubular heat-exchange passages
    • 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
    • F25B2309/003—Gas cycle refrigeration machines characterised by construction or composition of the regenerator
    • 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
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1415—Pulse-tube cycles characterised by regenerator details
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/006—Thermal coupling structure or interface

Definitions

  • This invention relates to cryogenic cooling systems and, in particular, to helium cooling systems embodying a regenerator.
  • such cooling systems are generally two-stage pulse tube, Stirling, or Gifford-McMahon type cooling systems having a first stage operating within a range of about 40K to about 100K and a second stage operating in the liquid helium temperature range, i.e. , about 2K to about 6K. It is generally desirable to reduce the parasitic heat load on the lowest temperature cooling stage to increase the overall efficiency of the system. Conventionally, this problem has been addressed by operating the first stage of the cooling system at the lowest achievable temperature, resulting in less heat being transferred to the second, or lower temperature, stage. Success by this method, however, is generally limited by the cooling capacity of the first, or upper temperature, stage. Furthermore, more inefficiency (e.g. , power and thermal inefficiencies) may result from this approach.
  • more inefficiency e.g. , power and thermal inefficiencies
  • the present invention is directed to overcoming, or at least reducing, the effects of one or more of the problems set forth above.
  • the invention concerns a cooling system according to claim 1.
  • the invention concerns also a method of operating a cooling system according to claim 11.
  • FIG 1 depicts an illustrative embodiment of a cooling system 100.
  • the cooling system 100 includes a compressor 102 in fluid communication with various helium gas flow control components, which are indicated generally as 104 in Figure 1 .
  • the flow control components 104 may include valves, orifices, reservoirs, and the like for controlling the flow of gaseous helium through the cooling system 100.
  • the cooling system 100 further includes a first regenerator 106 in fluid communication with at least some of the flow control components 104 and with a first pulse tube 108 via a tube or line 110.
  • the first regenerator 106 is a type of heat exchanger that absorbs heat from the helium during a first part of the pressure cycle and returns heat to the helium during a second part of the pressure cycle to enhance the cooling power of the helium.
  • the first pulse tube 106, and pulse tubes in general, function to cool the helium via changes in helium pressures therein.
  • the first regenerator 106, the first pulse tube 108, and the line 110 comprise an upper stage 112 of the cooling system 100.
  • helium gas flows through the first regenerator 106, the line 110, and into the first pulse tube 108.
  • the gas may also flow through an orifice and into a reservoir, which are included in the flow control components 104.
  • heat in the helium gas is moved from a first end 114 of the first pulse tube 108 toward a second end 116 of the first pulse tube 108, where it is removed.
  • temperatures proximate the first end 114 of the first pulse tube 108 may be greater than about 20K.
  • the cooling system 100 further includes a second regenerator 118 in fluid communication with the first stage 112 and with a second pulse tube 120 via a line 122.
  • the first regenerator 106 and the second regenerator 118 are shown in Figure 1 as being disposed in-line. However, those skilled in the art having benefit of the present disclosure would appreciate that the scope of the present invention is not so limited but rather may have any chosen spatial relationship between the first regenerator 106 and the second regenerator 118.
  • helium gas flows through the second regenerator 118, the line 122, and into the second pulse tube 120. In some embodiments, the gas may also flow through an orifice and into a reservoir, which are included in the flow control components 104.
  • temperatures proximate the first end 124 of the second pulse tube 120 may be within a range of about 2K to about 4K.
  • a heat exchanger 128 is disposed between a first portion 130 and a second portion 132 of the regenerator 118.
  • the heat exchanger 128 is disposed with a physical area or zone of the regenerator 118 that operates within a temperature of about 8K to about 20K.
  • the enthalpy difference of the helium is generally greatest within a temperature range of about 8K to about 20K.
  • variations in the helium enthalpy may lead to thermal irreversibilities as the regenerator 118 is operated based upon temperature gradients.
  • the regenerator 118 can become a source of cooling, via the heat exchanger 128, and the heat exchanger 128 extracts cooling power from helium flowing through the regenerator 118.
  • the second regenerator 118, the line 122, the second pulse tube 120, and the heat exchanger 128 comprise a lower stage 134 of the cooling system 100.
  • One or more various components 136 such as mechanical structures, electrical cabling, leads, thermal shields, and/or other components linking the second stage 134 and the first stage 112 or linking the second stage 134 and the surrounding environment may be thermally linked to the heat exchanger 128 via a thermal link 138.
  • the heat exchanger 128 may also be thermally coupled via a thermal link 202 to a thermal intercept 204 that is attached to, or inserted within, the second pulse tube 120.
  • the thermal intercept 204 is generally designed for transmitting heat from the second pulse tube 120 to the thermal link 202.
  • the thermal intercept 204 is attached to the second pulse tube 120 within a physical area or zone thereof that operates within a temperature range of about 8K to about 20K.
  • the thermal intercept 204 comprises a high thermally conductive material (e.g., copper, a copper alloy, aluminum, an aluminum alloy, or the like) wrapped around the second pulse tube 120 and/or inserted within the second pulse tube for more efficient thermal exchange.
  • the thermal intercept 204 has a configuration corresponding to that of the heat exchanger 128. In other words, the thermal intercept 204 may be disposed between two portions of the second pulse tube 120.
  • the thermal link 138 may comprise any desired thermally conductive structure for transmitting heat from the component 136 to the heat exchanger 128.
  • the thermal link 138 may comprise a metallic (e.g. , copper, a copper alloy, aluminum, an aluminum alloy, or the like) portion extending between the component 136 and the heat exchanger 128.
  • the thermal link may comprise a metallic (e.g., copper, a copper alloy, aluminum, an aluminum alloy, or the like) braid covering at least a portion of a cable or lead and extending to the heat exchanger 128.
  • the thermal link may, in one embodiment, comprise a heat pipe extending between the component 136 and the heat exchanger 128.
  • a heat pipe comprises a sealed container made of a high thermal conductivity material having inner surfaces with a capillary wicking material.
  • the heat exchanger 128 may comprise various configurations, such as those shown in Figures 3A-3F .
  • a first illustrative embodiment of the heat exchanger 128, shown in Figures 3A (front view) and 3B (side view) may comprise a plurality of plates 302 (only one is labeled for ease of illustration) defining a plurality of openings 304 (only one is labeled for ease of illustration) therethrough.
  • the openings 304 defined by each plate 302 are generally aligned to allow fluid flowing through the second regenerator 118 to communicate therethrough, so that heat may be transferred to the helium from the walls of the openings 304.
  • FIG. 3C front view
  • 3D side view
  • This second embodiment may comprise a block 306 defining a plurality of openings 308 (only one is labeled for ease of illustration) therethrough, such that fluid flowing through the second regenerator 118 may communicate through the openings 308.
  • the second embodiment may, in certain situations, have greater thermal exchange capabilities and than the first embodiment, since the second embodiment omits interfaces between the plates 302.
  • the heat exchanger 128 comprises a high thermal conductivity material, such as copper, a copper alloy, aluminum, or an aluminum alloy.
  • FIGS 3E (front view) and 3F (side view) depict a third illustrative embodiment of the heat exchanger 128, which comprises a grid 310 of thermally conductive material (e.g. , copper, a copper alloy, aluminum, an aluminum alloy, or the like).
  • the grid 310 defines openings 312 (only one indicated) that allow fluid flowing through the second regenerator 118 to communicate therethrough.
  • the third embodiment may, in certain situations, have greater thermal exchange capabilities over the first and second embodiments due to a greater amount of surface area over which helium may flow.
  • the thermal intercept 204 may have configurations corresponding to the embodiments of the heat exchanger 128 depicted in Figures 3A-3F .
  • the thermal intercept 204 may be disposed within the pulse tube 120 and comprise a plurality of plates defining a plurality of openings therethrough, a block defining a plurality of openings therethrough, or a grid defining a plurality of openings therethrough. In each case, openings allow helium to flow therethrough and a thermal exchange occurs between the helium and the walls of the openings.
  • heat exchanger 128, the thermal links 138, 202, and the thermal intercept 204 are shown in Figures 1-3F as being used with a pulse tube type cooling system, the present invention is not so limited. Rather the heat exchanger 128, the thermal links 138, 202, and the thermal intercept 204 may be used with any cooling system having a regenerator-type device, such as Stirling cooling systems and Gifford-McMahon cooling systems.
  • Figure 4A depicts a first illustrative embodiment of a method of extracting cooling power from helium in the regenerator 118.
  • the method includes flowing helium through the first portion 130 of the regenerator 118 (block 402) and flowing the helium through the heat exchanger 128 disposed between the first portion 130 and the second portion 132 of the regenerator 118 (block 404).
  • the method further includes transferring heat from the component 136 via the thermal link 138 to the heat exchanger 128 (block 406).
  • Figure 4B depicts a second illustrative embodiment of a method of extracting cooling power from helium in the regenerator 118 according to the present invention.
  • the method includes blocks 402, 404 as described above concerning Figure 4A .
  • the method according to the claimed invention further includes transferring heat from the thermal intercept 204 coupled with the pulse tube 120 to the heat exchanger 128 via the thermal link 202 (block 408). In this way, heat may be extracted from the pulse tube 120 to enhance its cooling capabilities.
  • Figure 4C depicts a third illustrative embodiment of a method of extracting cooling power from helium in the regenerator 118 according to the present invention.
  • the method includes blocks 402, 404 as described above concerning Figure 4A .
  • the method further comprises transferring heat from the thermal intercept 204 coupled with a zone of the pulse tube 120 capable of operating within a temperature range of about 8K to about 20K to the heat exchanger 128 via the thermal link 202 (block 410).
  • the cooling capability of the pulse tube 120 may be enhanced by taking advantage of the greatest enthalpy difference of helium within the pulse tube 120, which is within a temperature range of about 8K to about 20K.
  • Figure 4D depicts a fourth illustrative embodiment of a method of extracting cooling power from helium in the regenerator 118.
  • the method includes blocks 402, 406 as described above concerning Figure 4A .
  • the method further includes flowing helium having a temperature within a range of about 8K to about 20K through the heat exchanger 128, which is disposed between the first portion 130 and the second portion 132 of the regenerator 118.
  • the cooling capability of the helium within the regenerator 118 may be enhanced by taking advantage of the greatest enthalpy difference of helium therein, which is within a temperature range of about 8K to about 20K.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Magnetic Resonance Imaging Apparatus (AREA)

Claims (12)

  1. Kühlsystem (100), das Folgendes umfasst:
    mindestens einen Regenerator (118), der einen Durchfluss von Helium dadurch gestatten kann;
    einen in dem Regenerator angeordneten Wärmetauscher (128), der Kühlleistung aus dem Helium extrahieren kann; und
    eine an den Wärmetauscher gekoppelte thermische Verbindung (138) zur thermischen Kopplung des Wärmetauschers an eine Komponente (136), wobei das Kühlsystem (100) weiterhin ein Pulsationsrohr (120) umfasst;
    gekennzeichnet durch
    eine Wärmeunterbrechung (204), die thermisch an das Pulsationsrohr (120) gekoppelt ist; und
    eine an den Wärmetauscher (128) und an die Wärmeunterbrechung (204) gekoppelte thermische Verbindung (202).
  2. Kühlsystem nach Anspruch 1, wobei der Regenerator (118), der Wärmetauscher (128) und die thermische Verbindung (138) Teil einer unteren Stufe des Kühlsystems sind, wobei das System weiterhin eine obere Stufe zur Zufuhr von gekühltem Helium zur unteren Stufe umfasst.
  3. Kühlsystem nach Anspruch 1 oder 2, wobei die Komponente (136) eine Komponente des Kühlsystems umfasst.
  4. Kühlsystem nach einem der Ansprüche 1 - 3, wobei der Wärmetauscher (128) ein aus der aus Kupfer, einer Kupferlegierung, Aluminium und einer Aluminiumlegierung bestehenden Gruppe ausgewähltes Material umfasst.
  5. Kühlsystem nach einem der Ansprüche 1 - 4, wobei der Wärmetauscher (128) eine Struktur umfasst, die mehrere Öffnungen dadurch zur Übertragung des Heliums definiert, so dass Kühlleistung aus dem Helium extrahiert werden kann.
  6. Kühlsystem nach einem der Ansprüche 1 - 5, wobei die thermische Verbindung (138) ein Wärmerohr umfasst.
  7. Kühlsystem nach einem der Ansprüche 1 - 6, wobei der Wärmetauscher (128) in einem Bereich des Regenerators angeordnet ist, der in einem Temperaturbereich von ca. 8 K bis ca. 20 K betrieben werden kann.
  8. Kühlsystem nach einem der Ansprüche 1 - 7, wobei das Kühlsystem (100) ein Pulsationsrohrkühlsystem umfasst.
  9. Kühlsystem nach einem der Ansprüche 1 - 8, wobei das Kühlsystem (100) ein Stirling-Kühlsystem umfasst.
  10. Kühlsystem nach einem der Ansprüche 1 - 9, wobei das Kühlsystem (100) ein Gifford-McMahon-Kühlssystem umfasst.
  11. Verfahren zum Betrieb eines Helium als Arbeitsfluid zum Kühlen einer Vorrichtung (136) verwendenden Kühlsystems (100), wobei der Kühler eine erste und eine zweite Kühlstufe aufweist, die jeweils einen Regenerator (106, 118) aufweisen, wobei der Druck in der zweiten Stufe in einem Temperaturbereich zwischen 2 K und 50 K zwischen ca. 1 x 105 Pa und 1 x 106 Pa schwankt, mit dem Schritt des Herstellens einer Wärmeaustauschbeziehung zwischen einem Bereich des Regenerators (128) der zweiten Stufe, der eine Temperatur in einem ersten Temperaturbereich aufweist, und einer mechanischen Verbindung, die den Kühler mit der Vorrichtung (136) verbindet und eine mittlere Temperatur aufweist, die höher ist als der erste Temperaturbereich, wobei das Kühlsystem (100) weiterhin ein Pulsationsrohr (120) umfasst und gekennzeichnet ist durch eine Wärmeunterbrechung (204), die thermisch an das Pulsationsrohr (120) gekoppelt ist, und eine thermische Verbindung (202), die den Wärmetauscher (128) an die Wärmeunterbrechung (204) koppelt.
  12. Verfahren nach Anspruch 11, wobei der Bereich des Regenerators der zweiten Stufe so ausgewählt wird, dass er eine Arbeitstemperatur zwischen 8 und 20 K aufweist.
EP03076111A 2003-04-15 2003-04-15 Helium- Kühlanlage und zugehöriges Betriebsverfahren Expired - Lifetime EP1469261B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE60325333T DE60325333D1 (de) 2003-04-15 2003-04-15 Helium- Kühlanlage und zugehöriges Betriebsverfahren
AT03076111T ATE418049T1 (de) 2003-04-15 2003-04-15 Helium- kühlanlage und zugehöriges betriebsverfahren
EP03076111A EP1469261B1 (de) 2003-04-15 2003-04-15 Helium- Kühlanlage und zugehöriges Betriebsverfahren

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03076111A EP1469261B1 (de) 2003-04-15 2003-04-15 Helium- Kühlanlage und zugehöriges Betriebsverfahren

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EP1469261A1 EP1469261A1 (de) 2004-10-20
EP1469261B1 true EP1469261B1 (de) 2008-12-17

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EP (1) EP1469261B1 (de)
AT (1) ATE418049T1 (de)
DE (1) DE60325333D1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2914050B1 (fr) * 2007-03-21 2012-12-28 Air Liquide Refrigerateur a basse ou tres basse temperature et procede de refrigeration

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2856756A (en) * 1953-06-26 1958-10-21 Philips Corp Cold-gas refrigerating machine and method
NL140615B (nl) * 1965-04-06 1973-12-17 Philips Nv Inrichting voor het verwekken van koude bij zeer lage temperaturen.
US5298337A (en) * 1989-07-05 1994-03-29 Alabama Cryogenic Engineering, Inc. Perforated plates for cryogenic regenerators and method of fabrication
US5101894A (en) * 1989-07-05 1992-04-07 Alabama Cryogenic Engineering, Inc. Perforated plate heat exchanger and method of fabrication
KR940004233Y1 (ko) * 1991-05-15 1994-06-22 삼성전자 주식회사 열 압축식 히트 펌프
JP3674791B2 (ja) * 1994-07-14 2005-07-20 アイシン精機株式会社 冷却装置
US6173761B1 (en) * 1996-05-16 2001-01-16 Kabushiki Kaisha Toshiba Cryogenic heat pipe
JP4360020B2 (ja) * 2000-08-24 2009-11-11 アイシン精機株式会社 蓄冷式冷凍機

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DE60325333D1 (de) 2009-01-29
EP1469261A1 (de) 2004-10-20
ATE418049T1 (de) 2009-01-15

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