US3892106A - Method for reducing the consumption of a cryostat and a device for carrying out said method - Google Patents

Method for reducing the consumption of a cryostat and a device for carrying out said method Download PDF

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US3892106A
US3892106A US455004A US45500474A US3892106A US 3892106 A US3892106 A US 3892106A US 455004 A US455004 A US 455004A US 45500474 A US45500474 A US 45500474A US 3892106 A US3892106 A US 3892106A
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gas
heat exchanger
cryostat
chamber
pressure
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US455004A
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English (en)
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Pierre Roubeau
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Commissariat a lEnergie Atomique et aux Energies Alternatives CEA
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Commissariat a lEnergie Atomique CEA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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
    • 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

Definitions

  • This invention relates to a method for reducing the consumption of a cryostat in which it is desired to maintain a fluid in its liquid phase and to a device for carrying out said method.
  • the invention finds an application especially in the construction of a liquid helium economizer.
  • Economizers of known types make use of an auxiliary refrigeration circuit in which the gas is liquefied by the Joule-Thomson expansion process.
  • an auxiliary source of liquid with a view to supplying this latter to a heat exchanger which has the intended function of precooling the gas injected into the auxiliary refrigeration circuit in order to cause the temperature to fall below the inversion temperature.
  • the known economizer systems therefore call for a source of liquid ⁇ pipes for transferring said liquid between the source and the heat exchangers of the auxiliary refrigeration circuit, and a large number of siphons.
  • the corresponding installation is therefore cumbersome and, in the final analysis, the economy' which is achieved is of a very low order and rapidly' tends to fall to zero if the power of the installation is not of very high value.
  • This invention is directed to a method for reducing the consumption ofa cryostat and to a device for carrying out said method in which the disadvantages attached to known systems of this type are eliminated.
  • the present invention relates to a method for reducing the consumption of a cryostat in which a fluid is maintained in its liquid phase and cooled in accordance with said method by means of an auxiliary refrigeration circuit in which an identical fluid is liquefied by the method of isenthalpic expansion or so-called Joule-Thomson expansion process, characterized in that said auxiliary' refrigeration circuit is fed with gaseous fluid at a temperature which is higher than the Joule-Thomson effect inversion temperature in the case of said fluid and that the gaseous fluid which passes out of the cryostat itself serves to perform a contributory function in cooling said gaseous fluid supplied to the auxiliary refrigeration circuit and to cause the temperature of said gaseous fluid to drop below said inversion temperature,
  • the invention further relates to a device for reducing the consumption of fluid of a cryostat which serves to carry out the method hereinabove defined and comprises a refrigeration circuit of the type employed for liquefaction by Joule-Thomson expansion.
  • the economizer is characterized in that it comprises:
  • a heat exchanger comprising a high-pressure circuit supplied with gas from said source and a lowpressure circuit supplied both with the nonliquefied portion of the gas after expansion and with the vaporized portion of the liquid contained in the cryostat,
  • a gas expansion unit located at the outlet of said highpressure circuit.
  • the pressure P2 of the expanded gas at the outlet of said unit being the pressure which prevails within the cryostat.
  • the liquefied portion of said expanded gas being returned into the liquid contained in said cryostat.
  • the overall size of the assembly consisting of heat exchanger and expansion unit being sufficiently small to permit introduction of said assembly through the neck ofsaid cryostat which is sealed by means ofa leak-tight plug throuch which are passed the two circuits for the circulation of gases at the pressures P, and P.
  • the economizer is characterized in that it comprises:
  • a pump-compressor assembly' for sucking the gas at a pressure P'. I which is lower than atmospheric pressure and discharging said gas at a pressure P', which is higher than P'.
  • a condensation heat-exchanger through which circulates the gas discharged from the vaporization heat-exchanger, said gas being heated while condensing the vapors of the liquid of the cryo- Slal,
  • a low-pressure circuit through which passes the gas discharged from said condensation heatexchanger, said low-pressure circuit being in close thermal contact with said high-pressure circuit so as to constitute a main heat exchanger ⁇ said gas being subjected to a pressure drop AP- i within said low-pressure.
  • ⁇ circuit which delivers a gas to the pump-compressor assemblyl at thc pressure P-, P2 APL ⁇ a circuit for the flow of the vaporized portion of the liquid contained in said cryostat and at the pressure P;i in close thermal coupling with said high-pressure and Iowpressure circuits.
  • said vaporized portion being subjected within said circuit to a pressure drop AP so as to be discharged at the pressure P3 API, which is equal in particular to atmospheric pressure ⁇ the overall size of said heat-exchanger and expansionunit assembly being sufficiently' small to permit of in troduction of said assembly into the neck of said cryostat and this latter being closed by means of a leak-tight plug through which are passed the three circuits for the circulation of gases at the pressures P, AP,. P2 .AP-z ⁇ Ps Apri-
  • the expansion units employed can be either a capillary tube, an expansion valve. a porous medium. a throttle valve ⁇ or any other means of creating a backpressure by producing expansion as a result of a throttling or wiredrawing effect.
  • a part of the gas can be directed towards a compressor or a pumpcompressor assembly constituting the source of gas at the pressure P,.
  • Athe pump can be inde pendent ab@ the gas at the pssure P, can he supplied from a soue other than compressor.
  • FIG. l is a diagram of the device of the invention in accordance with the first alternative embodiment
  • FIG. 2 is a diagram of thc device of the invention in accordance with the second alternative embodiment'
  • FIG. 3 is a simplified diagram of a heat exchanger which can be employed in the first alternative ernbodiment
  • FIG. 4 shows a particular form of construction of the economizer in accordance with the second alternative embodiment ofthe invention
  • FIG. 5 shows two details A and B of the economizer of FIGY 4;
  • FIG. 6 shows two further details C and D ofthe same economizer.
  • the invention can be utilized for a wide range of different gases ⁇ the following description rcfers by way of explanation to a cryostat which contains liquid helium.
  • the inversion temperature of the Joule- Thomson effect in the case of helium is in the vicinity of 50K. Above this temperature. the helium therefore becomes heated upon expansion. However, this temperature rise is ofa very low order since it corresponds to an extremely small difference in specific heat between the gas under pressure and the expanded gas.
  • the difference in enthalpy' at 300K between the gas at IO atmospheres and the gas at OI atmosphere is approximately 3 J/g.
  • the helium injected into the economizer is at a temperature higher than 50K, for example at ambient temperature ⁇ it is therefore apparent that only a few frigories between 50K and ambient temperature will be necessary in order to Iiquefy said gas by the cumulative process of ⁇ lciuleThomson expansion.
  • the frigories aforesaid are taken from the helium gas which passes out of the c'ryostat and evaporates at 4K, for example.
  • the difference in enthalpy of the gas between 4K and 300K is approximately l600 J/g. It is therefore necessary to have only a very low gas flow rate in order to cool the gas introduced into the economizer to a suffcient extent to ensure that the Joule-Thomson expansion can produce a cooling action.
  • the cryostat 2 of the Dewar vessel type contains liquid helium 4.
  • a refrigeration circuit 8 is introduced into the neck 6 of said cryostat ⁇ said circuit being supplied from a source l0 of helium under pressure and at a temperature above the Joule-Thomson effect inversion temperature of helium.
  • the heat exchanger !2 comprises a high-pressure circuit 14 and a low-pressure circuit 16.
  • An expansion unit I8 is located at the extremity of the high-pressure circuit 14. On the downstream side of said expansion unit, the liquefied portion of the expanded helium is returned to the helium contained within the cryostat.
  • the low-pressure circuit I6 is fed with gas both from the non-liquefied portion of the gas after expansion of this latter through the expansion unit I8 and from the vaporized portion of the liquid 4 contained in the cryostat.
  • a plug 20 serves to close the vessel at the top of the neck.
  • the source I0 delivers helium at the pressure P, AP which is again present on the upstream side of the expansion unit at the pressure P,.
  • P2 On the downstream side of said unit the pressure above the liquid 4 is P2 and, at the outlet ofthe low-pressure circuit 16, the helium escapes at the pressure P2 AF2 which can be atmospheric pressure.
  • FIG. 2 ⁇ there is shown the device ofthe invention in accordance with the second alternative embodiment.
  • a pump-compressor assembly draws-up the gas at a pressure P2 APg and discharges the gas at a pressure PI AP,.
  • the helium then flows successively through the fol lowing units:
  • a vaporization heat-exchanger 56 in which the helium S8 which has been liquefied at the outlet of the expansion unit 54 is vaporized at the pressure P2 and cools the liquid 60 of the cryostat 62 or. if necessary and depending on the level of the liquid within the cryostat 62, condenses the vapors 64 of the evaporated liquid 60'.
  • a condensation heat-exchanger 66 in which that portion of the helium 58 which has vaporized within the heat exchanger 56 is heated from the temperature corresponding to the saturated vapor pressure P2 up to the ideal condensing vapor temperature corresponding to the pressure P.1 which prevails within the cryostat (and which can be in the vicinity of atmospheric pressure, for example), the temperature rise of said gas 30 being caused by condensation of part of the vapors 64 A of the main bath 60 which return to this latter in liquid form;
  • a low-pressure circuit 68 which forms in particular with the high-pressure circuit S2 a heat exchanger 70, 35
  • the vaporized portion 64 ofthe evaporated liquid 60 is discharged through a circuit 72 in which there is al pressure drop APH, with the result that the pressure of said vapor is caused to change from P3 to P3 AP the circuit 72 also forms part ⁇ of the h'eat exchanger '70.
  • the neck ofthe cryostat is closed by means of a plug 74.
  • the heat exchanger 12 is constituted by a hollow cylinder 30 and especially a metallic cylinder surrounding a plurality of tubes 32 which are fed in parallel with expanded gas at the pressure P2 (arrows 34); these hollow tubes constitute the secondary circuit of the heat exchanger.
  • the primary circuit is constituted by the space formed between the tubes 32 and the cylinder 30. This circuit is associated with an inlet 36 for the admission of4 gas at the pressure Pl -l- API and with an outlet 38 through which the gas is discharged at the pressure Pl and conveyed to the expansion unit 18,
  • the pressure drop is proportional to the fourth power ofthe reciprocal of the diameter it is shown by calculation, for example, that the diameter must be larger than 0.5 mm in order to have a pressure drop AP below 0.1 atmosphere with P2 l atmosphere and must be larger than 0.6 mm in order that AP should be below 0.08 atmosphere with P2 0.1 atmosphere.
  • the present Applicant has observed experimentally a pressure drop AP of 0.0025 atmosphere. Taking into account the above-mentioned law. the diameters usually employed will therefore be within the range of 0.5 to 0.7 mm.
  • FIG. 4 shows the cconomizer unit as a whole.
  • the helium is introduced through the high-pressure inlet which communicates with an admission tube 102.
  • the helium passes successively through the main heat exchanger 104, the tube 140, a porous medium 106 which performs the function of expansion unit, the vaporization heat-exchanger
  • the outlet 116 guides the gas as this latter passes 0 out of the main bath ofthe cryostat (not shown) which is assumed to surround the vaporization and condensation heat-exchangers 108 and 110; said gas is collected in the annular space formed between the tube 112 and the outer tube or shell 118 which are located within the bead of the cryostat.
  • FIG. 5 shows two details of the device of FIG. 4 as considered at the levels A and B. ln FlG. SA, the highpressure gas is admitted through the tube 102 at the pressure P, -l- API. At the extremity 120, said highpressure gas spreads out and circulates within the shell 160 between the tubes 122 through which the lowpressure helium circulates in the opposite direction and is discharged at the extremities 124 at the pressure P2 AF2.
  • the helium which leaves the main bath of the cryostat flows through a small number of pressure-drop tubes AP3, only one tube 126 being shown in FIG. 5. Said helium is discharged at the pressure P:L AP into the cham ber formed by the two rings or tube sheets 130 and 132 and escapes through the orifice 134 into the annular space formed between the cylinders 112 and 1 18.
  • the high-pressure gas which circulates between the tubes 122 is returned through the tube 140 at the level ofthe ring or tube sheet 142.
  • the helium which is evaporated from the main bath at the pressure P3 penetrates into the circuit through the orifice 144, then into the tubes 126.
  • FIG. 5 ⁇ the references 143 and 145 designate respectively one of the spacer rings or tube sheets and a central rod which is intended to prevent any preferential llow along the axis ⁇
  • FIG. 6 illustrates two details at the levels C and D.
  • the high-pressure gas is admitted through the tube 140.
  • the expanded gas at the pressure P2 is collected at the extremities 150 of the tubes 122 in the proximity of thc ring or tube sheet 152.
  • the so-called condensation heat-exchanger is therefore provided between the rings 142 and 152.
  • the condensed liquid escapes through the orifice 154 and is returned to the main bath.
  • the expansion unit 106 of FIG. 6D is fed with helium at the pressure Pl through the tube 140. Expansion takes place through three washers 158 ofsintered stainless steel. The liquefied portion of the helium is collected at the lower end of the shell 160 which constitutes the so-called vaporization heat-exchanger 108.
  • the tubes 122, 126, 140 and 160 are advantageously of stainless steel, the thickness of the tube walls being between O.l and 0.2 mm.
  • the rings or tube sheets 130, 132, 142 and 152 are of copper and are brazed to the stainless steel tubes.
  • the tubes 122 which constitute the low-pressure circuit have the same cross-section from one end of the heatexchanger to the other. It is possible in an improved am rangement to make use of smaller tubes in the lower portion ofthe heat exchanger in which the temperature is at its lowest value since the pressure drop varies approximately as the square of the temperature. ln this case ⁇ the tubes 122 can have a minimum diameter which is two to three times smaller within said lower portion.
  • An auxiliary refrigeration unit for reducing the consumption ofa fluid existing in liquid and vapor phases within a cryostat the unit adapted to be connected to a source of high pressure fluid for supply at a temperature which is higher than the Joule-Thomson effect inversion temperature of the fluid, comprising:
  • a hollow cylinder adapted to be disposed in the cryostat and having an inlet connected to the source of pressurized gas to establish a high pressure flow circuit for the pressurized gas, a gas expansion unit connected to the outlet of said cylinder for expanding said pressurized gas in accordance with the Joule-Thomson effect.
  • the pressure of the expanded gas at the outlet of said unit being at the pressure which prevails within the cryostat, and the liquefied portion of said expanded gas being returned into the liquid contained in said cryostat, and
  • a plurality of tubes extending through said cylinder and adapted to receive both the nonliquefled portion of said gas after expansion and the vaporized portion of the liquid contained in the cryostat to establish a low pressure flow circuit for said portions arid pass said portions in a heat exchange relation to said pressurized gas passing through said cylinder.
  • An auxiliary' refrigeration unit for reducing the consumption ofa fluid existing in liquid and vapor phases within a cryostat. including a heat exchanger and expansion unit assembly' adapted to be connected to a pump-compressor assembly of the type having a gas inlet and a gas outlet for supplying high pressure gas at a temperature above its Joule-Thomson effect inversion temperature.
  • said h'eat exchanger and expansion unit assembly comprising:
  • a plurality of tube sheets said tube sheets dividing said cylindrical shell into a plurality of chambers including an inlet chamber having means for connection to the outlet of the pump compressor assembly; an outlet chamber having means for connection to the inlet of the pump-compressor assembly' ⁇ a main heat exchanger chamber; a condensation heat exchanger chamber; and a vaporization heat exchanger chamber; said cylindrical shell having formed therein a plurality of apertures for permitting entry of a portion ofthe vapor from within the cryostat into said condensation heat exchanger chamber; a plurality oflongitudinal parallel low pressure circuit tubes connecting said outlet chamber with said vaporization heat exchanger chamber, said low pressure circuit tubes extending through said main heat exchanger chamber and said condensation heat exchanger chamber to divide the space within said main heat exchanger chamber and said Condensation heat exchanger chamber into shell sides and tube sides;
  • a gas expansion unit connected to said main heat exchanger outlet tube and being disposed within said vaporization heat exchanger chamber.
  • a jacket mounted on said cylindrical shell for defining a vapor collection space around said cylindrical shell and adjacent said vapor circuit chamber, said jacket having vapor inlet means Communicating with the shell side of said vapor circuit chamber and vapor discharge means;
  • a vapor circuit tube connecting said condensation heat exchanger chamber with said vapor circuit chamber and extending through said main heat ex changer chamber.
  • auxiliary refrigeration unit defined by claim 2 further including means mounted within said main heat exchanger chamber for preventing preferrential flow of the high pressure fluid through said shell side of said main heat exchanger chamber.
  • auxiliary refrigeration unit defined by claim 2 wherein said jacket which defines said vapor collection space comprises a cylindrical housing having a diamc- 5 ter greater than the diameter of said cylindrical shell, said cylindrical housing being mounted concentric with said cylindrical shell and between said vapor circuit chamber and said outlet chamber.
  • a device for reducing the consumption of a cryostat containing a fluid in a liquid phase comprising:
  • a hollow cylinder disposed in said Cryostat and having an inlet for receiving said fluid in the form of a gas under pressure and at a temperature which is higher than the Joule-Thomson effect inversion temperature of said gas
  • a gas expansion unit connected to the outlet of said cylinder for expanding said pressurized gas in ac cordance with the Joule-Thomson effect.
  • the pressure of the expanded gas at the outlet of said unit being at the pressure which prevails within the cryostat.
  • a vaporization heat-exchanger disposed in said cryostat and connected to said gas expansion unit for vaporizing that portion of the gas which has liquefied after passing through the expansion unit while cooling the liquid in the cryostat and/or while condensing the vapors of the liquid of said cryostat,
  • a condensation heat-exchanger disposed in said cryostat and connected to said vaporization heat exchanger for receiving the gas discharged from the vaporization heat-exchanger and the vapors of the liquid of the cryostat. and passing said gas and said vapors in a heat exchange relation to heat said gas and condense said vapors,
  • a pump-compressor assembly for drawing the heated gas from said condensation heat exchanger and pressurizing said gas.
  • the outlet of said assembly being connected to said inlet of said cylinder, and
  • a first and second series of tubes extending through said cylinder and adapted to receive the gas from said gas expansion unit and the vaporized portion of the liquid contained in the cryostat ⁇ respectively.
  • said tubes being adapted to pass said gas and said vaporized portion in a heat exchange relation to said pressurized gas passing through said cylinder.
  • a flow circuit connects said condensation heat exchanger to said pump compressor assembly and passes said heated gas in a 50 heat exchange relationship to the pressurized gas passing through said cylinder and to said gas and said vaporized portion passing through said tubes,

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Measuring And Other Instruments (AREA)
US455004A 1973-03-27 1974-03-26 Method for reducing the consumption of a cryostat and a device for carrying out said method Expired - Lifetime US3892106A (en)

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FR7310885A FR2288956A1 (fr) 1973-03-27 1973-03-27 Procede de reduction de la consommation d'un cryostat et dispositif correspondant

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US (1) US3892106A (xx)
JP (1) JPS49128342A (xx)
BE (1) BE811978A (xx)
DE (1) DE2412905C2 (xx)
FR (1) FR2288956A1 (xx)
GB (1) GB1433727A (xx)
IT (1) IT1011633B (xx)
NL (1) NL7404050A (xx)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0158395A1 (en) * 1984-03-29 1985-10-16 Koninklijke Philips Electronics N.V. Method of liquefying a gas and liquefier for carrying out the method
US4920753A (en) * 1987-08-04 1990-05-01 Canon Kabushiki Kaisha Method of storing volatile substances, container for storing said substances, and flow-control method for surface flow of superfluid helium
EP1197716A1 (en) * 1998-12-25 2002-04-17 Japan Science and Technology Corporation Liquid helium recondensation device and transfer line used therefor
US20070209371A1 (en) * 2006-03-13 2007-09-13 Raytheon Company MIXED GAS REFRIGERANT SYSTEM FOR SENSOR COOLING BELOW 80ºK
US20120180899A1 (en) * 2009-09-29 2012-07-19 Koninklijke Philips Electronics N.V. Sytem and method for liquefying a fluid and storing the liquefied fluid

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3435229A1 (de) * 1984-09-26 1986-04-03 Kernforschungszentrum Karlsruhe Gmbh, 7500 Karlsruhe Kryostat fuer den betrieb einer (pfeil hoch)3(pfeil hoch)he-(pfeil hoch)4(pfeil hoch)he-mischeinheit
JPS63129280A (ja) * 1986-11-18 1988-06-01 株式会社東芝 ヘリウム冷却装置
ES2510290B2 (es) * 2013-03-20 2015-04-30 Emilio PALOMO PINTO Sistema de refrigeración autónomo, portátil y autorefrigerante, basado en la utilización de un depósito estanco, conteniente de un gas licuado a presión, empleado como vaporizador, como consecuencia de la evaporación controlada de dicho GLP

Citations (4)

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US2895303A (en) * 1956-05-17 1959-07-21 Little Inc A Purification of low-boiling gases
US3415077A (en) * 1967-01-31 1968-12-10 500 Inc Method and apparatus for continuously supplying refrigeration below 4.2deg k.
US3422632A (en) * 1966-06-03 1969-01-21 Air Prod & Chem Cryogenic refrigeration system
US3704601A (en) * 1969-03-25 1972-12-05 Hymatic Eng Co Ltd Cryogenic cooling apparatus

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DE345052C (de) * 1916-12-01 1921-12-05 Lilienfeld Dr Wasserstoffverfluessiger
GB861111A (en) * 1958-12-01 1961-02-15 Hughes Aircraft Co Gas liquefaction apparatus
GB863961A (en) * 1959-01-23 1961-03-29 Hymatic Eng Co Ltd Improvements relating to gas liquefiers
FR1439668A (fr) * 1965-07-09 1966-05-20 Hughes Aircraft Co Cryostat à circuit fermé
BE758030A (fr) * 1969-10-28 1971-04-26 Philips Nv Installation pour produire du froid aux temperatures inferieures a celles du point lambda de l'helium
DE2009401A1 (de) * 1970-02-27 1971-09-09 Linde Ag, 6200 Wiesbaden Verfahren zum Verflüssigen tiefsie dender Gase

Patent Citations (4)

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Publication number Priority date Publication date Assignee Title
US2895303A (en) * 1956-05-17 1959-07-21 Little Inc A Purification of low-boiling gases
US3422632A (en) * 1966-06-03 1969-01-21 Air Prod & Chem Cryogenic refrigeration system
US3415077A (en) * 1967-01-31 1968-12-10 500 Inc Method and apparatus for continuously supplying refrigeration below 4.2deg k.
US3704601A (en) * 1969-03-25 1972-12-05 Hymatic Eng Co Ltd Cryogenic cooling apparatus

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0158395A1 (en) * 1984-03-29 1985-10-16 Koninklijke Philips Electronics N.V. Method of liquefying a gas and liquefier for carrying out the method
US4920753A (en) * 1987-08-04 1990-05-01 Canon Kabushiki Kaisha Method of storing volatile substances, container for storing said substances, and flow-control method for surface flow of superfluid helium
US5065583A (en) * 1987-08-04 1991-11-19 Canon Kabushiki Kaisha Method of storing volatile substances, container for storing said substances, and flow-control method for surface flow of superfluid helium
EP1197716A1 (en) * 1998-12-25 2002-04-17 Japan Science and Technology Corporation Liquid helium recondensation device and transfer line used therefor
EP1197716A4 (en) * 1998-12-25 2002-10-02 Japan Science & Tech Corp APPARATUS FOR CONDENSING LIQUID HELIUM AND TRANSFER DUCT USED FOR THIS PURPOSE
EP1477755A1 (en) * 1998-12-25 2004-11-17 Japan Science and Technology Corporation Liquid helium recondensation device and transfer line used therefor
US20070209371A1 (en) * 2006-03-13 2007-09-13 Raytheon Company MIXED GAS REFRIGERANT SYSTEM FOR SENSOR COOLING BELOW 80ºK
US20120180899A1 (en) * 2009-09-29 2012-07-19 Koninklijke Philips Electronics N.V. Sytem and method for liquefying a fluid and storing the liquefied fluid
US9841228B2 (en) 2009-09-29 2017-12-12 Koninklijke Philips N.V. System and method for liquefying a fluid and storing the liquefied fluid

Also Published As

Publication number Publication date
FR2288956A1 (fr) 1976-05-21
BE811978A (fr) 1974-07-01
IT1011633B (it) 1977-02-10
JPS49128342A (xx) 1974-12-09
FR2288956B1 (xx) 1978-06-23
DE2412905A1 (de) 1974-10-10
NL7404050A (xx) 1974-10-01
DE2412905C2 (de) 1985-09-26
GB1433727A (en) 1976-04-28

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