EP1586833A2 - Kühlvorrichtung - Google Patents

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Publication number
EP1586833A2
EP1586833A2 EP05251855A EP05251855A EP1586833A2 EP 1586833 A2 EP1586833 A2 EP 1586833A2 EP 05251855 A EP05251855 A EP 05251855A EP 05251855 A EP05251855 A EP 05251855A EP 1586833 A2 EP1586833 A2 EP 1586833A2
Authority
EP
European Patent Office
Prior art keywords
coolant
heat exchanger
refrigerator
supply line
cryostat
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.)
Withdrawn
Application number
EP05251855A
Other languages
English (en)
French (fr)
Other versions
EP1586833A3 (de
Inventor
Oleg Kirichek
Gregory Kouzmenko
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.)
Oxford Instruments Superconductivity Ltd
Original Assignee
Oxford Instruments Superconductivity Ltd
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 Oxford Instruments Superconductivity Ltd filed Critical Oxford Instruments Superconductivity Ltd
Publication of EP1586833A2 publication Critical patent/EP1586833A2/de
Publication of EP1586833A3 publication Critical patent/EP1586833A3/de
Withdrawn legal-status Critical Current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
    • F25B9/02—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
    • 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
    • F25B2400/17—Re-condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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

  • the invention relates to cooling apparatus, for example for use in cooling electrical conductors to a temperature at which they superconduct.
  • the invention is particularly suited for cooling electromagnets to their superconducting condition for use in NMR (nuclear magnetic resonance) and ICR (ion cyclotron resonance) experiments.
  • 2.2K is the preferred operating temperature for two reasons.
  • the specific heat capacity of 4 He peaks at the ⁇ point (Fig. 2), so it is desirable to operate as near the lambda point as possible to improve the temperature stability of the system.
  • it is generally considered undesirable to operate below the ⁇ point. This is because a proportion of the liquid becomes superfluid, with zero viscosity, and it will flow, even against gravity, through the smallest cracks and orifices towards areas of the cryostat at higher temperature, thus causing a large heat leak and increasing boil-off (the so-called "superleak” phenomenon).
  • a "lambda point refrigerator” has been used.
  • a magnet 2 is submerged in liquid He in a first coolant containing vessel 1 at atmospheric pressure.
  • a second coolant containing vessel 3 which is open to atmosphere, holds a reservoir of liquid He boiling at 4.2K; this reservoir 3 may be refilled at any time. It is connected to the vessel 1 via a quench valve 14.
  • Liquid He is conveyed from the second vessel 3 to a heat exchanger 5 in the first vessel 1 via an (optional) second heat exchanger 6 and an expansion valve 4.
  • the heat exchanger 5 is typically a coiled loop tube immersed in the top of the liquid helium bath of the first vessel 1.
  • the pressure in the loop 5, on the downstream side of the valve 4, is reduced by pumping using an external pump 13, typically to 20-50mbar.
  • Helium liquid passing through the valve 4 is partially vaporized and cooled by a few Kelvin due to the pressure drop across the valve.
  • the reduced vapour pressure in the loop lowers the boiling temperature of the remaining liquid, which consequently evaporates, absorbing heat from the magnet bath and cooling it via heat exchange through 5.
  • the vapour leaving the heat exchanger 5 is passed through the optional second heat exchanger 6, which pre-cools the liquid entering the valve with the aim of reducing the fraction vaporized in the valve, and hence reducing the mass flow rate required for a given cooling power.
  • the cooling power of the lambda point refrigerator constituted by components 4,5,6 is given by: where dm/dt is the total mass flow rate, H is enthalpy and ⁇ is the fraction of liquid flashed to vapour in the valve.
  • cryostat 20 comprising a number of shields to be described below.
  • the cold vapour leaving the second heat exchanger 6 passes up the cryostat 20 though another heat exchanger 10, absorbing heat from a gas cooled shield 7, which sits at a temperature at about 40K, and then through a final heat exchanger 11, absorbing heat from the second shield 8.
  • the shields 7,8 of the cryostat 20 reduce the radiation heat load on the helium vessels 1 & 3, reducing total boil-off. Because the outer shield 8 sees the largest radiation load, it is common for it to have supplementary cooling from nitrogen boiling at atmospheric pressure (77K) in a vessel 8a thermally connected to the shield 8.
  • the entire vessel assembly is enclosed in an evacuated vessel 9 to reduce conduction and convection loss.
  • the magnet 2 and inner vessels are typically suspended using a web of fibreglass rods (not shown) to reduce conduction heat load.
  • a bore tube (not shown) at room temperature and pressure passes through the assembly and through the magnet bore 22 to allow samples to be placed inside the magnet 2.
  • the helium gas After passing through a pump 13 located outside the cryostat 20 the helium gas is either vented to atmosphere and lost, or collected for later re-use (after reliquefaction in a separate plant).
  • the spring-closed pop-off valve 14 allows the boiling helium in the first vessel 1 to escape to the second vessel 3, and hence to atmosphere, before a dangerous over-pressure condition develops.
  • cooling apparatus comprises a cooling system defining a closed path around which a coolant flows, the system including a pump for causing coolant flow, a supply line extending from the pump to a cold location, positioned in a cryostat, in order to cool that location, and a return line extending from the cold location to the pump, the pump being located externally of the cryostat; a first heat exchanger positioned within the cryostat and linking the supply and return lines to allow heat exchange therebetween such that coolant flowing in the supply line is cooled by coolant flowing in the return line; and a refrigerator having a cooling stage within the cryostat and coupled to the supply line downstream of the first heat exchanger such that coolant reaching the first cooling stage has been precooled by the first heat exchanger.
  • the solution involves utilizing a refrigerator having at least one cooling stage and assisting that cooling stage by including the first heat exchanger so as to precool the coolant before it reaches the first cooling stage. This reduces the power requirement of the first cooling stage to such an extent that conventional refrigerators such as pulse tube refrigerators, can be used.
  • the cooling system includes a lambda point refrigerator located at the cold location while the cold location may be located within an auxiliary coolant containing vessel. Alternatively, an item to be cooled could be connected directly to the closed path of the cooling system.
  • the apparatus further comprises a second heat exchanger, located within the cryostat, and linking the supply and return lines such that coolant flowing in the supply line is cooled by coolant flowing in the return line, the second heat exchanger being upstream of the first heat exchanger with respect to coolant flow direction along the supply line.
  • the use of the second heat exchanger enables additional precooling to be achieved thus further producing the power requirements on the refrigerator.
  • further heat exchangers could be provided if required.
  • a single stage refrigerator can be used but in the preferred examples, the refrigerator has an additional cooling stage, warmer than the one coolant stage, the additional cooling stage being located within the cryostat and being coupled to the supply line to cool the supply line at a location upstream of the first heat exchanger.
  • the refrigerator has an additional cooling stage, warmer than the one cooling stage, the additional cooling stage being located within the cryostat and being coupled to a shield of the cryostat so as to cool the shield.
  • the additional cooling stage cools both coolant in the supply line and the shield.
  • this is preferably located upstream of the one cooling stage of the refrigerator with respect to the direction of flow of coolant along the supply line.
  • the coolant which flows in the closed path of the cooling system comprises He although other coolants could be used depending upon the temperature required at the cold location.
  • An alternative, for example is nitrogen.
  • the refrigerator is typically an electrically powered mechanical refrigerator such as a pulse tube refrigerator since this has minimum vibration problems.
  • a pulse tube refrigerator any cooler providing a low temperature cold stage and where coolant (such as 4 He) is consumed, could be used. Therefore, alternatives to pulse tube refrigerators include Stirling, Gifford-McMahon, Joule-Thomson refrigerators, dilution refrigerators and so on.
  • the cooling apparatus can be utilized to cool a variety of objects but it is particularly suited to the cooling of electrical conductors to their superconducting condition as required, for example, in NMR, MRI and ICR where superconducting magnets are required.
  • the magnets will define a bore, typically at room temperature and the surrounding vessels will be shaped to allow remote access to the bore.
  • a closed cooling system is provided defined by a supply line 26 extending from the pump 13 via a pump filter 13a into the cryostat 20 to the lambda refrigerator 4-6 and a return line 28 extending from the lambda refrigerator back to the pump 13.
  • the supply line 26 opens into the second vessel 3 and is coupled to a second stage 16 of a two stage pulse tube refrigerator (PTR) 24.
  • PTR pulse tube refrigerator
  • This second stage 16 recondenses helium vapour which boils in the vessel 3 and also condenses helium supplied along the supply line 26. It absorbs typically a few 10s to 100s mW of power.
  • the supply line Prior to reaching the second stage 16 of the PTR 24, the supply line extends through a "first" heat exchanger 17 which links the supply line 26 with the return line 28.
  • This heat exchanger 17 allows the cold returning helium in the return line 28 to cool helium being supplied along the supply line 26 prior to reaching the first cooling stage 15. This reduces the cooling power required at the first cooling stage 15.
  • This first heat exchanger 17 is particularly important because it keeps the cooling power requirement of the second stage 16 of the PTR 24 below about 1W (the limit of current PTR technology at 4.2K).
  • a "second" heat exchanger 19 is provided upstream of the heat exchanger 17 with respect to the supply line.
  • the heat exchanger 19 allows further heat exchange between the supply and return lines 26,28 so as to further precool the helium in the supply line.
  • a "third" heat exchanger 18 is provided coupled between the supply line 26 and the shield 8.
  • the shield 8 is connected to a first stage 15 of the PTR 24 which is used to cool the outer shield 8 to about 40K, requiring about 30W for a typical large NMR magnet system. In view of these connections, the first stage 15 of the PTR 24 cools both the shield 8 and helium in the supply line 26.
  • the heat exchangers 17 and 19 utilise the enthalpy of the cold gas leaving the lambda point refrigerator that, in the prior-art system, was used to cool the shields 7 and 8.
  • the heat exchanger 18 adds a small heat load (a few watts) to the first stage 15 of the PTR 24.
  • the invention provides a zero boil-off (ZBO) system consuming no helium in normal operation and thus providing significant advantages of no disruptive and costly refilling being required.
  • ZBO zero boil-off
  • the cooling power of the outgoing helium flow does not need to be utilized for cooling any radiation shields (unlike in the prior art) since the first stage 15 achieves this cooling, this cooling power can be used to pre-cool the incoming helium flow.
  • the circulation of outgoing and return or incoming flows is the same and so pre-cooling of the return flow from 45K down to about 5K can be achieved using the heat exchanger 17.
  • the heating power required at the second stage 16 can be reduced to about 0.3-0.45W.
  • Such powers are readily available from commercially available pulse tube refrigerators.
  • the system shown in the drawings can be used to cool a variety of items but particularly superconducting magnets which may be used in any conventional configuration such as MRI, NMR, and ICR.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetic Resonance Imaging Apparatus (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
EP05251855A 2004-04-14 2005-03-24 Kühlvorrichtung Withdrawn EP1586833A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB0408312.7A GB0408312D0 (en) 2004-04-14 2004-04-14 Cooling apparatus
GB0408312 2004-04-14

Publications (2)

Publication Number Publication Date
EP1586833A2 true EP1586833A2 (de) 2005-10-19
EP1586833A3 EP1586833A3 (de) 2006-10-11

Family

ID=32320814

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05251855A Withdrawn EP1586833A3 (de) 2004-04-14 2005-03-24 Kühlvorrichtung

Country Status (4)

Country Link
US (1) US20050229609A1 (de)
EP (1) EP1586833A3 (de)
JP (1) JP2005351613A (de)
GB (1) GB0408312D0 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2433581A (en) * 2005-12-22 2007-06-27 Siemens Magnet Technology Ltd Closed-loop pre-cooling of cryogenically cooled equipment
WO2011112987A3 (en) * 2010-03-11 2012-11-08 Quantum Design, Inc. Method and apparatus for controlling temperature in a cryocooled cryostat using static and moving gas
US20130160975A1 (en) * 2011-12-22 2013-06-27 General Electric Company Thermosiphon cooling system and method
GB2502628A (en) * 2012-06-01 2013-12-04 Stfc Science & Technology Cryostat having a multistage cryocooler with a terminal cooling chamber thermally coupled to the final cooling stage
EP4033176A4 (de) * 2019-11-01 2022-12-07 Japan Superconductor Technology Inc. Vorrichtung zur rekondensation von helium für kryostaten

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US7318318B2 (en) * 2004-03-13 2008-01-15 Bruker Biospin Gmbh Superconducting magnet system with refrigerator
GB0411607D0 (en) * 2004-05-25 2004-06-30 Oxford Magnet Tech Recondenser interface
JP5540642B2 (ja) * 2009-10-07 2014-07-02 富士電機株式会社 超電導機器の冷却装置
CN102054555B (zh) * 2009-10-30 2014-07-16 通用电气公司 超导磁体的制冷系统、制冷方法以及核磁共振成像系统
US20130047632A1 (en) * 2010-05-03 2013-02-28 Consejo Superior De Investigaciones Cientificas (Csic) Gas liquefaction system and method
US10690387B2 (en) 2010-05-03 2020-06-23 Consejo Superior De Investigaciones Científicas (Csic) System and method for recovery and recycling coolant gas at elevated pressure
DE102010028750B4 (de) * 2010-05-07 2014-07-03 Bruker Biospin Gmbh Verlustarme Kryostatenanordnung
TWI571941B (zh) * 2010-05-12 2017-02-21 布魯克機械公司 用於低溫冷卻的系統及方法
DE102011013577B4 (de) * 2011-03-10 2013-02-28 Karlsruher Institut für Technologie Vorrichtung zur Speicherung von Wasserstoff und von magnetischer Energie sowie ein Verfahren zu ihrem Betrieb
GB2493553B (en) * 2011-08-11 2017-09-13 Oxford Instr Nanotechnology Tools Ltd Cryogenic cooling apparatus and method
DE102012201108A1 (de) * 2012-01-26 2013-08-01 Siemens Aktiengesellschaft Vorrichtung zur Kühlung einer supraleitenden Maschine
CN103077797B (zh) * 2013-01-06 2016-03-30 中国科学院电工研究所 用于头部成像的超导磁体系统
US20140202174A1 (en) * 2013-01-24 2014-07-24 Cryomech, Inc. Closed Cycle 1 K Refrigeration System
US20150075183A1 (en) * 2013-09-16 2015-03-19 Bruker Biospin Corporation Polarization insert for a cryogenic refrigerator
JP6286242B2 (ja) * 2014-03-18 2018-02-28 株式会社日立製作所 超電導磁石装置
DE102014225481A1 (de) * 2014-12-10 2016-06-16 Bruker Biospin Gmbh Kryostat mit einem ersten und einem zweiten Heliumtank, die zumindest in einem unteren Bereich flüssigkeitsdicht voneinander abgetrennt sind
EP3163222B1 (de) * 2015-10-28 2018-07-18 Technische Universität München Kältemittelfreie kühlvorrichtung
US11248996B2 (en) 2017-12-04 2022-02-15 Montana Instruments Corporation Analytical instruments, methods, and components
US10724780B2 (en) * 2018-01-29 2020-07-28 Advanced Research Systems, Inc. Cryocooling system and method
EP3850264A4 (de) * 2018-09-12 2022-03-02 The Regents Of The University Of Colorado Kryogenisch gekühlte vakuumkammerstrahlungsschilde für ultratieftemperaturexperimente und für bedingungen mit extrem hohem vakuum (xhv)
US11956924B1 (en) 2020-08-10 2024-04-09 Montana Instruments Corporation Quantum processing circuitry cooling systems and methods
CN112885554B (zh) * 2021-02-19 2023-06-02 西安聚能超导磁体科技有限公司 一种小型高温超导直冷磁体及其装配方法

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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2433581A (en) * 2005-12-22 2007-06-27 Siemens Magnet Technology Ltd Closed-loop pre-cooling of cryogenically cooled equipment
JP2007205709A (ja) * 2005-12-22 2007-08-16 Siemens Magnet Technology Ltd 極低温に冷却される機器の閉ループ予冷方法及び装置
GB2433581B (en) * 2005-12-22 2008-02-27 Siemens Magnet Technology Ltd Closed-loop precooling of cryogenically cooled equipment
CN101106006B (zh) * 2005-12-22 2011-10-05 英国西门子公司 低温冷却的设备的闭环预冷
CN102290187A (zh) * 2005-12-22 2011-12-21 英国西门子公司 低温冷却的设备的闭环预冷
GB2490836A (en) * 2010-03-11 2012-11-14 Quantum Design Inc Method and apparatus for controlling temperature in a cryocooled cryostat using static and moving gas
WO2011112987A3 (en) * 2010-03-11 2012-11-08 Quantum Design, Inc. Method and apparatus for controlling temperature in a cryocooled cryostat using static and moving gas
CN102971594A (zh) * 2010-03-11 2013-03-13 量子设计有限公司 用于使用静态和移动气体来控制低温的低温恒温器中的温度的方法和设备
US20130160975A1 (en) * 2011-12-22 2013-06-27 General Electric Company Thermosiphon cooling system and method
US9958519B2 (en) * 2011-12-22 2018-05-01 General Electric Company Thermosiphon cooling for a magnet imaging system
GB2502628A (en) * 2012-06-01 2013-12-04 Stfc Science & Technology Cryostat having a multistage cryocooler with a terminal cooling chamber thermally coupled to the final cooling stage
EP4033176A4 (de) * 2019-11-01 2022-12-07 Japan Superconductor Technology Inc. Vorrichtung zur rekondensation von helium für kryostaten
US11828513B2 (en) 2019-11-01 2023-11-28 Japan Superconductor Technology Inc. Apparatus for recondensing helium for cryostat

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GB0408312D0 (en) 2004-05-19
JP2005351613A (ja) 2005-12-22
EP1586833A3 (de) 2006-10-11
US20050229609A1 (en) 2005-10-20

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