WO2002001123A1 - Echangeurs thermiques flexibles a contre-courant - Google Patents

Echangeurs thermiques flexibles a contre-courant Download PDF

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Publication number
WO2002001123A1
WO2002001123A1 PCT/US2001/040849 US0140849W WO0201123A1 WO 2002001123 A1 WO2002001123 A1 WO 2002001123A1 US 0140849 W US0140849 W US 0140849W WO 0201123 A1 WO0201123 A1 WO 0201123A1
Authority
WO
WIPO (PCT)
Prior art keywords
flexible
heat exchanger
return tube
refrigeration system
supply tubes
Prior art date
Application number
PCT/US2001/040849
Other languages
English (en)
Inventor
William A. Little
Original Assignee
Mmr Technologies, Inc.
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 Mmr Technologies, Inc. filed Critical Mmr Technologies, Inc.
Priority to AU2001267028A priority Critical patent/AU2001267028A1/en
Publication of WO2002001123A1 publication Critical patent/WO2002001123A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
    • 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
    • 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
    • F28D7/10—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 arranged one within the other, e.g. concentrically
    • F28D7/12—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 arranged one within the other, e.g. concentrically the surrounding tube being closed at one end, e.g. return type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • 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
    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61B—DIAGNOSIS; SURGERY; IDENTIFICATION
    • A61B18/00—Surgical instruments, devices or methods for transferring non-mechanical forms of energy to or from the body
    • A61B18/02—Surgical instruments, devices or methods for transferring non-mechanical forms of energy to or from the body by cooling, e.g. cryogenic techniques
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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

Definitions

  • Refrigeration systems are employed in a variety of applications that require cryogenic environments .
  • US Patent 5,337,572 describes a single compressor cryogenic refrigeration system; and US Patents 5,617,739 and 5,724,832 describe self-cleaning refrigeration systems suitable for operation at cryogenic temperatures.
  • Critical to the operation of these refrigerators is a counter-flow heat exchanger that is required to pre-cool a high-pressure supply refrigerant stream with a cooler, low-pressure return refrigerant stream. The latter has been passed through a flow-restrictor , causing it to drop in pressure and consequently to cool.
  • the low-pressure refrigerant is then used to cool a cold stage that is in contact with the object to be cooled, before returning to a compressor module by way of the heat exchanger.
  • Different versions of the heat exchanger can be used. In most cases the heat exchanger is placed in close proximity to the cold stage.
  • the compressor module including a compressor, an oil separator, a condenser and, in some systems a fractionating column, is connected to the heat exchanger via a long "umbilical cord" containing separate high-pressure supply and low-pressure return lines.
  • the umbilical cord is generally made to be flexible and entirely at ambient temperature, thereby requiring no insulation.
  • the heat exchanger itself is contained in a vacuum-insulated (or other type of thermally- insulated) enclosure that can be quite bulky.
  • the heat exchanger can be located in the compressor module.
  • the umbilical cord in this case contains the high-pressure supply and the cooler low-pressure return lines, both of which must be insulated from ambient temperature. This is typically done by the use of a vacuum- insulated, flexible hose.
  • the disadvantage of this approach is that the heat exchanger does not immediately precede the cold stage. That is, the supply refrigerant stream, after being cooled by the heat exchanger, still needs to traverse a considerable distance, and consequently incurs unwanted thermal losses before entering the cold stage.
  • OBJECTS AND ADVANTAGES Accordingly it is a principal object of the present invention to provide a flexible and modular heat exchanger that extends from the compressor module of a refrigeration system to the cold stage and allows counter-flow heat exchange along the entire connection. It is a further object of the present invention to provide methods for manufacturing such a heat exchanger and for coupling the heat exchanger to the refrigeration system.
  • An important advantage of the present invention is that by using the flexible heat exchanger both as a hose bridging the cold stage and the compressor module and as a heat exchanger, the refrigeration system becomes more compact, modular, and more efficient.
  • Another advantage of the present invention is that it frees up space in the vicinity of the cold stage, thus allowing the cold stage to be more compact in size. Further advantages of the heat exchanger of the present invention are manifest in its simple design, ease of repair, and adaptability for a variety of applications .
  • This invention describes a flexible heat exchanger that provides both a direct connection between a cold stage and a compressor module of a refrigeration system and heat exchange along the entire connection.
  • a flexible heat exchanger plays a dual role as a hose connecting the cold stage with the compressor module, and as a heat exchanger, itself.
  • the need for a cumbersome heat exchanger at one end or the other of the connecting link (between the compressor module and the cold stage) , and additional connecting lines between the heat exchanger and the compressor module (or the cold stage) are eliminated.
  • the flexibility of the heat exchanger makes the corresponding refrigeration system modular and easily adaptable to different applications. Further, counter-flow heat exchange between the supply and return refrigerant streams takes place along the length between the compressor and the cold stage, thereby maximizing the efficiency of heat transfer.
  • One end of the heat exchanger is designed to be coupled to the compressor module, while the other end is coupled to the cold stage of the refrigeration system.
  • the coupling means hereof can be made to be adaptable and removable, making the repair of the heat exchanger and the transportation of the refrigeration system much easier.
  • FIG. 1 shows an exemplary representation of a refrigeration system according to the present invention
  • FIG. 2 depicts a cross-sectional view of an exemplary embodiment of a heat exchanger according to the present invention
  • FIGS. 3A-3B depict side views of two exemplary embodiments of a heat exchanger according to the present invention
  • FIG. 4 provides an exemplary embodiment illustrating how a plurality of high-pressure supply lines (contained within the low-pressure return line) are combined to provide a common connection at the compressor module end of the heat exchanger, or at the cold stage end of the heat exchanger.
  • FIG. 1 depicts an exemplary embodiment of a refrigeration system 100 according to the present invention.
  • a compressor module 10 and a cold stage 11 are bridged by a flexible heat exchanger 12. More specifically, a first end 13 of the heat exchanger 12 is coupled to the compressor module 10, and a second end 14 of the heat exchanger 12 is coupled to the cold stage .
  • the length between the first end and the second end of the heat exchanger can be up to several meters, and is typically about 3 meters.
  • FIG. 2 depicts a cross-sectional view of a first exemplary embodiment of the heat exchanger 12 shown in FIG . 1.
  • the heat exchanger 12 comprises a flexible outer jacket 20, typically made of bellows or helical tubing about 2 cm (e.g., 3/4") in inner-diameter (ID) and 2.5 cm (1") in outer-diameter (OD) .
  • the outer jacket is commonly made of stainless steel, or bronze.
  • a flexible return tube 21 typically made of bellows or helical tubing of about 1 cm (e.g., 3/8") in ID and 1.6 cm (0.64") in OD.
  • the return tube is generally made of copper, bronze, or stainless steel.
  • the return tube 21 may be further provided with a braided outer cover to prevent it from changing length with variations in the return refrigerant pressure.
  • a plurality of flexible high-pressure supply tubes 22 are preferably made of fully annealed stainless steel, with 0.1 cm (e.g., 0.04") ID and 0.16 cm (1/16") OD, to provide the necessary flexibility.
  • the supply tubes can be made of copper, bronze, nickel, or cupro-nickel tubing.
  • the space between the return and supply tubes constitutes a low-pressure return line 23.
  • the supply tubes 22 are disposed within, and completely surrounded by the return line 23.
  • the supply tubes 22 As a warm, high-pressure input refrigerant stream passes through the supply tubes 22, it is cooled by a counter-flow of cold, low-pressure return refrigerant stream along the return line 23.
  • the use of a plurality of small diameter supply tubes also provides greater flexibility than a single, larger diameter tube.
  • a space 24 between the outer jacket 20 and the return tube 21 is thermally insulated, usually through a vacuum. This is achieved by evacuating and subsequently sealing off the outer jacket 20, or by connecting one end of the outer jacket 20 to a vacuum system.
  • the return tube 21 may be further insulated by wrapping it in several layers of superinsulation, or aluminized mylar ribbon 25.
  • FIG. 3A provides a side view of a second exemplary embodiment of the heat exchanger shown in FIG. 1, along with the corresponding refrigeration system 101.
  • the first ends 13A of the high-pressure supply tubes 22 and the first end 13B of the return tube 21 at the first end 13 (comprising 13A, 13B) of the heat exchanger 12 are connected to the high-pressure outlet and the low-pressure inlet of the compressor module 10, respectively.
  • the second end 14 (comprising 14A, 14B) of the heat exchanger 12 the second end 14B of the return line 21 is coupled to the cold stage 11, and the second ends 14A of the high-pressure supply tubes 22 are coupled to a flow restrictor 15 in the cold stage 11.
  • the first ends 13A, 13B of the heat exchanger 12 are at ambient temperature, generally between about 273 and 330 K; and the second end 14B of the return line 21 of the heat exchanger 12 is at a cryogenic temperature, ranging from about 70 to 200 K.
  • Vacuum insulation is commonly used to provide thermal insulation of the cold stage as well as of the heat exchanger by extending the outer jacket 20 to enclose the sections of the cold stage that are at cryogenic temperatures.
  • a counter-flow of high-pressure supply and low-pressure return refrigerant streams takes place along all supply tubes 22 within the insulated enclosure provided by the outer jacket 20, extending from the compressor module 10 to the flow restrictor 15.
  • FIG. 3B provides a side view of a third exemplary embodiment of the heat exchanger shown in FIG. 1, along with the corresponding refrigeration system 102.
  • a second flow restrictor 16 is disposed within the heat exchanger 12, coupled to the second ends 14A' of one or more auxiliary high-pressure supply tubes 22 ', while the supply tubes 22 continue to be coupled to the flow restrictor 15 in the cold stage 11.
  • the purpose of the second flow restrictor 16 is to let the high-pressure refrigerant stream carried by the auxiliary supply tubes 22 ' to expand and consequently to cool .
  • the cooled low-pressure refrigerant then returns to the compressor module 10 via the return line 21 and pre-cools the incoming high-pressure refrigerant stream along the way.
  • the first ends 13A, ISA' of the supply tubes 22, 22 ' and the first end 13B of the return tube 21 at the first end 13 (comprising 13A, 13A' , 13B) of the heat exchanger 12 are connected to the high-pressure outlet and the low-pressure inlet of the compressor module 10, respectively.
  • the second end 14 (comprising 14A, 14B) of the heat exchanger 12 is coupled to the cold stage 11, and the second ends 14A of the high-pressure supply tubes 22 are coupled to the flow restrictor 15.
  • the first ends 13A, 13A', 13B of the heat exchanger 12 are typically at ambient temperature, approximately between 273 and 330 K; and the second end 14B of the return line 21 of the heat exchanger 12 is at a cryogenic temperature, ranging from 70 to 200 K.
  • Vacuum insulation is generally used to provide thermal insulation of the cold stage 11 as well as of the heat exchanger by extending the outer jacket 20 to enclose the sections of the cold stage that are at cryogenic temperatures.
  • the coupling between the heat exchanger 12 and the compressor module 10 and that between the heat exchanger 12 and the cold stage 11 in FIG. 1 may be achieved as follows.
  • the high-pressure supply tubes 22 and/or 22 ' are first combined at each end with suitable fittings, to provide a common feed line from the high-pressure outlet of the compressor module 10 and a common connection to the flow restrictor 15 in the cold stage 11.
  • the return tube 21 of the heat exchanger 12 then connects with an outlet of the cold stage 11 at one end and with the low-pressure inlet of the compressor module 10 at the other by means of brazing, welding, or removable connectors (e.g., SwageLock Quick Connects: SS-QC4-D-PM, SS-QC-B1-400 , B-QC4-B1-400 , B-QC-D- 400, and B-DC4-D-2HC) .
  • SwageLock Quick Connects SS-QC4-D-PM, SS-QC-B1-400 , B-QC4-B1-400 , B-QC-D- 400, and B-DC4-D-2HC
  • FIG. 4 provides an exemplary embodiment of a coupling means for combining the high-pressure supply lines (contained within the low-pressure return line) to form a common connection at the compressor module end of the heat exchanger, or at the cold stage end of the heat exchanger.
  • a plurality of high-pressure supply lines 30 are first brazed to a flange 31, which is in turn brazed into a fitting 32.
  • An outgoing line 33 is then brazed to the fitting 32, connecting the high-pressure supply lines to the compressor module, or to the flow restrictor in the cold stage.
  • the flange 31 is typically made of brass.
  • the fitting 32 is generally made of copper, or brass.
  • the outgoing line 33 can be made of copper, or stainless steel tubing .
  • heat exchanger of the present invention is made to be flexible and/or conformable.
  • the latter implies that the heat exchanger returns substantially to its original shape when the stress is removed; while in the case of the former, the heat exchanger retains its bent shape.
  • Both entail the use of a heat exchanger that can be bent to conform to a particular shape, and/or is capable of responding to the stress of bending or twisting by deforming .
  • the outer jacket 20 of the heat exchanger 12 can be made of unbraided, helical or bellows corrugated hose that is commercially available from Pacific Flex, Inc., Pacific Coast Cryogenics, 1600 Shasta Avenue,. San Jose, CA 95128.
  • a hose can yield considerable curvature along its length when being bent, and the degree of curvature varies with its size.
  • the minimum radius of curvature i.e., the most severe deformation
  • the return tube 21 can be a flexible helical or bellows tubing, made of copper, bronze, or stainless steel. It can also be a conformable tubing, comprising a material selected from the same group.
  • the high-pressure supply tubes 22, 22' are generally made of a material selected from the group consisting of stainless steel, copper, bronze, nickel, and cupro-nickel . The choice of the material and sizes of the supply tubes is such that they can be made flexible, and/or conformable. Those skilled in the art will know how to implement other types of tubing to make the heat exchanger flexible and to meet the need of a particular application.
  • the specific dimensions of the outer jacket, return and supply tubes described above provide only one exemplary embodiment of the heat exchanger of the present invention, suitable to work with a cold stage operating in a temperature range between 70 K and 200 K. It is known in the art of cryogenics that the physical dimensions and other characteristics of a heat exchanger depend upon the specific type of refrigeration system and in particular, the range of cryogenic temperatures the refrigeration system is intended to provide. Accordingly, a skilled artisan will know how to calculate the physical dimensions of the supply and return lines to achieve the desired heat exchange for a particular refrigerant to be used in the heat exchanger of a given application.
  • the advantages of the heat exchanger according to the present invention are apparent: being flexible, it makes a refrigeration system highly modular and adaptable to various applications; it provides an effective heat exchange along the way between the compressor module and the cold stage; it frees up the space in the vicinity of the cold stage; and it can be easily repaired should damage occur. Accordingly, it is ideally suited for a variety of applications, such as cryosurgery, cooling of electronic devices, and cooling of computer chips, etc.
  • the application of the heat exchanger of the present invention is not limited to cryogenic systems . It can also be employed in other applications involving the transfer of heat energy between two fluids .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur thermique flexible (12) qui établit à la fois une connexion directe entre un étage froid (11) et un module compresseur (10) d'un système frigorifique (100) et un échange thermique à contre-courant sur toute la connexion. L'invention concerne également des procédés permettant de fabriquer ledit échangeur thermique (120) et de l'intégrer dans des systèmes frigorifiques (100). La présente invention permet d'obtenir des systèmes frigorifiques (100) modulaires et facilement adaptables, un étage froid (11) de taille compacte et un échange thermique à contre-courant efficace.
PCT/US2001/040849 2000-06-23 2001-06-04 Echangeurs thermiques flexibles a contre-courant WO2002001123A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2001267028A AU2001267028A1 (en) 2000-06-23 2001-06-04 Flexible counter-flow heat exchangers

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US59948200A 2000-06-23 2000-06-23
US09/599,482 2000-06-23

Publications (1)

Publication Number Publication Date
WO2002001123A1 true WO2002001123A1 (fr) 2002-01-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2001/040849 WO2002001123A1 (fr) 2000-06-23 2001-06-04 Echangeurs thermiques flexibles a contre-courant

Country Status (2)

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AU (1) AU2001267028A1 (fr)
WO (1) WO2002001123A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1422486A2 (fr) * 2002-11-25 2004-05-26 Tempia Co., Ltd. Installation de chauffage et de réfrigération à régénération combinée
DE102005052290B4 (de) * 2004-11-05 2008-01-03 General Motors Corp. (N.D.Ges.D. Staates Delaware), Detroit Verwendung von Z-Rohren in einem Flüssigwasserstofftank
WO2009140066A1 (fr) * 2008-05-12 2009-11-19 Boston Scientific Scimed, Inc. Appareil pour refroidir un fluide de refroidissement de cryoablation
WO2012006645A3 (fr) * 2010-07-12 2012-11-22 Johannes Wild Dispositif de refroidissement
US8386258B2 (en) 2000-07-31 2013-02-26 Shazam Investments Limited Systems and methods for recognizing sound and music signals in high noise and distortion
WO2014111726A1 (fr) * 2013-01-18 2014-07-24 Soltropy Limited Améliorations apportées ou se rapportant à des systèmes de chauffage et de refroidissement
EP2420772A3 (fr) * 2010-07-12 2014-12-10 Johannes Wild Tête de refroidissement pour une installation de refroidissement
US11747076B2 (en) 2020-08-18 2023-09-05 Ajay Khatri Remote cooling of super-conducting magnet using closed cycle auxiliary flow circuit in a cryogenic cooling system

Citations (5)

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Publication number Priority date Publication date Assignee Title
US3626987A (en) * 1968-10-03 1971-12-14 Kabelund Metallwerke Ag Coaxial pipe system with thermal insulation
US3726321A (en) * 1971-02-19 1973-04-10 Dayco Corp Flexible hose
US4616196A (en) * 1985-01-28 1986-10-07 Rca Corporation Microwave and millimeter wave switched-line type phase shifter including exponential line portion
US5337572A (en) * 1993-05-04 1994-08-16 Apd Cryogenics, Inc. Cryogenic refrigerator with single stage compressor
US5617739A (en) * 1995-03-29 1997-04-08 Mmr Technologies, Inc. Self-cleaning low-temperature refrigeration system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3626987A (en) * 1968-10-03 1971-12-14 Kabelund Metallwerke Ag Coaxial pipe system with thermal insulation
US3726321A (en) * 1971-02-19 1973-04-10 Dayco Corp Flexible hose
US4616196A (en) * 1985-01-28 1986-10-07 Rca Corporation Microwave and millimeter wave switched-line type phase shifter including exponential line portion
US5337572A (en) * 1993-05-04 1994-08-16 Apd Cryogenics, Inc. Cryogenic refrigerator with single stage compressor
US5617739A (en) * 1995-03-29 1997-04-08 Mmr Technologies, Inc. Self-cleaning low-temperature refrigeration system

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9401154B2 (en) 2000-07-31 2016-07-26 Shazam Investments Limited Systems and methods for recognizing sound and music signals in high noise and distortion
US10497378B2 (en) 2000-07-31 2019-12-03 Apple Inc. Systems and methods for recognizing sound and music signals in high noise and distortion
US9899030B2 (en) 2000-07-31 2018-02-20 Shazam Investments Limited Systems and methods for recognizing sound and music signals in high noise and distortion
US8386258B2 (en) 2000-07-31 2013-02-26 Shazam Investments Limited Systems and methods for recognizing sound and music signals in high noise and distortion
US8700407B2 (en) 2000-07-31 2014-04-15 Shazam Investments Limited Systems and methods for recognizing sound and music signals in high noise and distortion
EP1422486A3 (fr) * 2002-11-25 2004-11-17 Tempia Co., Ltd. Installation de chauffage et de réfrigération à régénération combinée
EP1422486A2 (fr) * 2002-11-25 2004-05-26 Tempia Co., Ltd. Installation de chauffage et de réfrigération à régénération combinée
DE102005052290B4 (de) * 2004-11-05 2008-01-03 General Motors Corp. (N.D.Ges.D. Staates Delaware), Detroit Verwendung von Z-Rohren in einem Flüssigwasserstofftank
US7363775B2 (en) 2004-11-05 2008-04-29 General Motors Corporation Use of Z-pipes in a liquid hydrogen tank
US9655668B2 (en) 2008-05-12 2017-05-23 Boston Scientific Scimed, Inc. Apparatus and method for chilling cryo-ablation coolant and resulting cryo-ablation system
US9028445B2 (en) 2008-05-12 2015-05-12 Frank W. Ingle Apparatus and method for chilling cryo-ablation coolant and resulting cryo-ablation system
WO2009140066A1 (fr) * 2008-05-12 2009-11-19 Boston Scientific Scimed, Inc. Appareil pour refroidir un fluide de refroidissement de cryoablation
EP2420772A3 (fr) * 2010-07-12 2014-12-10 Johannes Wild Tête de refroidissement pour une installation de refroidissement
US9851126B2 (en) 2010-07-12 2017-12-26 Johannes Wild Cooling apparatus
WO2012006645A3 (fr) * 2010-07-12 2012-11-22 Johannes Wild Dispositif de refroidissement
WO2014111726A1 (fr) * 2013-01-18 2014-07-24 Soltropy Limited Améliorations apportées ou se rapportant à des systèmes de chauffage et de refroidissement
US11747076B2 (en) 2020-08-18 2023-09-05 Ajay Khatri Remote cooling of super-conducting magnet using closed cycle auxiliary flow circuit in a cryogenic cooling system

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