EP4495511A1 - Kryogenkühlsystem - Google Patents

Kryogenkühlsystem Download PDF

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Publication number
EP4495511A1
EP4495511A1 EP23187129.4A EP23187129A EP4495511A1 EP 4495511 A1 EP4495511 A1 EP 4495511A1 EP 23187129 A EP23187129 A EP 23187129A EP 4495511 A1 EP4495511 A1 EP 4495511A1
Authority
EP
European Patent Office
Prior art keywords
cryogen
cooling
cooling chamber
fluid
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Withdrawn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
EP23187129.4A
Other languages
English (en)
French (fr)
Inventor
Eoin HODGE
Emiliano Frulloni
Antoine Diana
Peter Stringer
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.)
Supernode Ltd
Original Assignee
Supernode 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 Supernode Ltd filed Critical Supernode Ltd
Priority to EP23187129.4A priority Critical patent/EP4495511A1/de
Priority to PCT/EP2024/070611 priority patent/WO2025021707A1/en
Publication of EP4495511A1 publication Critical patent/EP4495511A1/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Withdrawn legal-status Critical Current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
    • F25B19/00—Machines, plants or systems, using evaporation of a refrigerant but without recovery of the vapour
    • F25B19/005—Machines, plants or systems, using evaporation of a refrigerant but without recovery of the vapour the refrigerant being a liquefied gas
    • 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
    • F25D3/00—Devices using other cold materials; Devices using cold-storage bodies
    • F25D3/10—Devices using other cold materials; Devices using cold-storage bodies using liquefied gases, e.g. liquid air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01B—CABLES; CONDUCTORS; INSULATORS; SELECTION OF MATERIALS FOR THEIR CONDUCTIVE, INSULATING OR DIELECTRIC PROPERTIES
    • H01B12/00—Superconductive or hyperconductive conductors, cables, or transmission lines
    • H01B12/16—Superconductive or hyperconductive conductors, cables, or transmission lines characterised by cooling

Definitions

  • This invention relates to a cryogen cooling system for use in cooling cryogenic fluids, for example as used for cooling superconducting cables, and in particular a cryogen cooling system which utilises a venturi pump to effect a temperature reduction of the cryogenic fluid.
  • At least one electrically conducting element must be maintained at temperatures below the material transition temperature (T c ) to enable superconductivity.
  • T c material transition temperature
  • Superconductor transition temperatures vary from T c ⁇ 10 K for classic metallic superconductors up to values of T c > 100 K for ceramic high-temperature superconductors (HTS).
  • cryogens such as liquefied gases (Hydrogen, Oxygen, Nitrogen, etc.) are used as cooling mediums to achieve and maintain these temperatures within superconductor systems. It is critical to maintain the HTS core temperature at a sufficiently low value to ensure that a suitable superconducting state is maintained, otherwise the tapes become resistive, develop heat through Joule heating leading to rising temperature and a potential catastrophic runaway situation.
  • Standard superconductor cable systems use a forced flow, subcooled, single-phase cryogenic fluid such as liquid nitrogen or helium to absorb and evacuate excess thermal energy in order to maintain operational temperatures.
  • the cryogen is circulated within the system to achieve cooling using standard pressurization systems. Excess heat must be removed from the cryogen to maintain a liquefied state for continuous operation and avoid vaporization, which can be achieved through intermittent sub-coolers or cryocoolers. Increased system length necessitates both increased flow rates and system pressures to convey the cryogen which in turn increases the heat load due to the addition of frictional heating. This increases the requirements on heat removal systems and subsequent costs. Over extended distances (>2km) standard forced flow systems quickly prove uneconomical due to the high costs and low efficiency of the intermittent cooling stations.
  • cryogen transport pipelines may comprise an inner cryostat for conveying the liquid cryogen, surrounding by one or more layers of insulation.
  • a cryogen cooling system comprising a cryostat containing a supply of cryogen; a cooling chamber through which at least a portion of the cryogen is arranged to pass; and a venturi pump operable to reduce pressure within the cooling chamber in order to effect cooling of the passing cryogen.
  • the fluid flow path extending through the cooling chamber defines a heat exchanger.
  • the fluid flow path through the cooling chamber is in fluid isolation from, and in thermal communication with, the interior of the cooling chamber.
  • the cooling chamber comprises a bath of cooling fluid through which the fluid flow path extends and which is operable to undergo evaporative cooling in response to the reduced pressure established by the venturi pump.
  • the bath of cooling fluid comprises cryogen supplied from the fluid flow path.
  • venturi pump is driven by a supply of fluid derived from the bath of cooling fluid within the cooling chamber.
  • the cooling system comprises a venturi supply line extending from the cooling chamber to the venturi pump and arranged so that the cooling chamber and part of the venturi supply line provide a pressure head in the venturi supply line sufficient to operate the venturi pump.
  • the cryogen cooling system comprises a fluid driven motor on the venturi supply line upstream of the venturi pump.
  • the fluid flow path through the cooling chamber is in fluid and thermal communication with an interior of the cooling chamber.
  • the fluid flow path through the cooling chamber comprises an evaporator providing fluid communication between the fluid flow path and the cooling chamber and operable to effect evaporation of the cryogen in response to passage through the evaporator.
  • the evaporator comprises an array of nozzles operable to effect evaporation of the cryogen in response to passage through the nozzles.
  • the evaporator comprises a porous material.
  • the fluid flow path comprises a cryostat.
  • the cryostat passes through the cooling chamber.
  • the cryostat is located remotely of the cooling chamber, the fluid flow path comprising a supply line for transferring cryogen from the cryostat to the cooling chamber and a return line for transferring cryogen from the cooling chamber back to the cryostat.
  • venturi pump is driven by a supply of fluid derived from the cryogen within the cryostat.
  • the cryogen cooling system comprises a venturi supply line extending from the cryostat to the venturi pump.
  • the cryogen cooling system comprises a fluid driven motor on the venturi supply line upstream of the venturi pump.
  • the cryogen cooling system comprises at least one thermoelectric device operable to convert a temperature differential generated by the cryogen in order to provide a local power source.
  • a superconducting cable system comprising a superconductor and a cryogen cooling system according to the first aspect of the invention, wherein the supply of cryogen is in thermal communication with the superconductor.
  • the term “cable” is intended to cover both subsea and subterranean power cables in addition to above ground or overhead power lines.
  • venturi pump is intended to mean a negative pressure generating pump which utilises the flow of a fluid, Optionally a gas, along a primary flow path which includes a constriction, throat or choke section, from which constriction a secondary flow path extends and in which a negative pressure is established as a result of the flow of fluid through the constriction and which can therefore be used as a vacuum pump.
  • cryogen cooling system 10 may form part of a superconducting cable system for use in electrical power transmission and in particular over relatively long distances.
  • the cryogen cooling system 10 may also be used for cooling a liquid cryogen during pipeline transport over relatively long distances, for example liquid nitrogen, hydrogen, oxygen, which may be used as fuel or in other applications.
  • the cryogen cooling system 10 comprises an elongate cryostat C defining at least a part of a fluid flow path for the liquid cryogen.
  • the cryostat C may be part of a superconducting cable including superconducting material cooled by the liquid cryogen conveyed through the cryostat C alongside or surrounding the superconducting material.
  • the cryogen is in thermal and optionally physical communication with the superconducting material in order to be capable of maintaining the temperature thereof at the requisite operating temperature, for example between 63 and 77 Kelvin in the case of a high temperature superconducting material. It will of course be understood that this is an exemplary temperature and is not essential to the operation of the present invention. Alternatively, in liquid cryogen transport applications no such superconducting material is present and the liquid cryogen is simply transported through the cryostat C which therefore defines a transport pipeline for the cryogen. While the following embodiments are described primarily with respect to superconducting cable applications it is to be understood that cryogen transport applications are equally applicable.
  • a cooling chamber 12 in the form of a pressure resistant vessel is provided, externally of the cryostat, and through which at least a portion of the working cryogen from the cryostat C is diverted in order to cool the cryogen back down to the above mentioned operating temperature before being reintroduced into the cryostat C.
  • a cryogen supply line 14 extends from the cryostat C into the cooling chamber 12 while a cryogen return line 16 extends from the cooling chamber 12 back to the cryostat C, effectively forming an extension of the fluid flow path defined by the cryostat C.
  • the supply line 14 and return line 16 may be provided on a joint assembly (not shown) connecting two lengths of the cryostat C or may otherwise be arranged to divert the working cryogen from the cable cryostat C at appropriate locations along the length of the cable.
  • the supply line 14 may take cryogen at one joint (not shown) while the return line 16 may be feed cryogen back in at another joint on the cable.
  • a cooling element 18 extends through the interior of the cooling chamber 12 between the supply line 14 and the return line 16 to form a portion of the cryogen fluid flow path.
  • the cooling element 18 is a simple fluid tight tube which is optionally undulating or coiled in order to increase the length of the fluid flow path defined by the cooling element 18.
  • the cryogen flow path from the supply line 14, through the cooling element 18 and through the return line 16 is in fluid isolation from the interior of the cooling chamber 12, but is in thermal communication therewith, for example by means of the material selected for at least the cooling element 18, namely a thermally conductive material.
  • the interior of the cooling chamber 12 is at least partially filled with a cooling fluid 20, optionally the same cryogen flowing through the cryostat C, such that the cooling element 18 is at least partially and optionally completely immersed in the cooling fluid.
  • the cooling element 18 of the fluid flow path thus effectively defines a heat exchanger operable to transfer heat from the cryogen flowing through the fluid flow path defined by the cooling element 18 into the cooling fluid 20.
  • a fill line 22 may be provided from the supply line 14 to the cooling chamber 12 in order to fill and maintain the level of cooling fluid 20 in the cooling chamber 12. Suitable flow controls (not shown) such as valves or the like may be provided on the fill line 22 in order to manage the flow rate of cooling fluid into the cooling chamber 12.
  • the cryostat C is continuous between the supply line 14 and return line 16, particularly in the case of superconducting cable applications, with electrically conducting superconducting material S shown as a broken line to illustrate that the cryostat C extends between the supply line 14 and return line 16 in order to enclose the superconducting material S.
  • this continuity is not a requirement and could be omitted given that the liquid cryogen can flow uninterrupted along the flow path defined by the supply line 14, cooling element 18 and return line 16. This arrangement applies equally to the embodiments of Figures 2 , 3 and 7 as described hereinafter.
  • the cooling system 10 further comprises a venturi pump 24 having an inlet 26 and outlet 28 across which a fluid, for example compressed air or any other suitable fluid, may be driven in order to create a reduced pressure region at a throat of the venturi pump 24, from which a low pressure suction line 30 is connected to the cooling chamber 12, optionally at a upper portion in which a head space 32 is formed above the bath of cooling fluid 20.
  • a fluid for example compressed air or any other suitable fluid
  • the compressed air or other fluid may be supplied from any suitable location.
  • the compressed air may be provided from an onshore location, or from a floating platform or the like, for example produce from power generated from a floating wind turbine or the like.
  • the venturi pump 24 can then be utilised to create a reduced pressure within the cooling chamber 12, for example 200mbar, in order to effect evaporative cooling of the bath of cooling fluid 20.
  • the pressure established in the cooling chamber 12 may be carefully controlled, for example by the design and operation of the venturi pump 24, to ensure that the temperature of the cooling fluid 20 is maintained at the correct level to achieve the desired cooling of the cryogen flowing through the cooling element 18.
  • the fill line 22 can be operated to maintain a set level of cooling fluid 20 within the cooling chamber 12.
  • the fill line 22 is operated to extract approximately 10% of the cryogen from the cryostat C in order to replace the evaporated cooling fluid 20.
  • venturi pump 24 is located externally of the cooling chamber 12 it is also envisaged that the venturi pump 24 could be located within the cooling chamber 12, in particular in the head space 32. In that configuration the suction line 30 could be omitted as the throat of the venturi pump 24 is in direct fluid communication with the head space 32.
  • This alternative arrangement could equally be employed in any embodiment in which the cooling chamber has a bath of cooling fluid and a headspace above same.
  • the temperature of the cryogen returned to the cryostat C through the return line 16 can be maintained at the necessary level by means of the cooling chamber 12 and venturi pump 24 which do not include any moving parts, thus greatly improving the reliability of the cooling process.
  • FIG. 2 there is illustrated a second embodiment of a cryogen cooling system, generally indicated as 110, for use in electrical power transmission and optionally over relatively long distances, or in liquid cryogen transport.
  • a cryogen cooling system generally indicated as 110
  • like components have been accorded like reference numerals and unless otherwise stated perform a like function.
  • the cooling system 110 comprises a cryostat C, a cooling chamber 112 into which extends a supply line 114 from the cryostat C and out of which runs a return line 116 back to the cryostat C, with a cooling element 118 connected therebetween within the interior space of the cooling chamber 112.
  • the cooling element 118 is in the form of a coiled or corrugated tube of thermally conductive material, the cooling chamber 112 being filled with a cooling fluid 120 to immerse the cooling element 118.
  • the cryostat C, supply line 114, cooling element 118 and return line 116 define a fluid flow path along which a liquid cryogen is conveyed and which is in fluid isolation from, but in thermal communication with, the cooling fluid 120 within the interior of the cooling chamber 112.
  • a fill line 122 is provided between the supply line 114 and the cooling chamber 112 in order to allow the level of the cooling fluid 120 to be maintained despite evaporation during use.
  • a venturi pump 124 is provided, with an inlet 126 being connected via a venturi supply line 140 to a base of the cooling chamber 112 such that the cooling fluid 120 is then used as the source of driving fluid for the venturi pump 124.
  • the venturi supply line 140 extends below the cooling chamber 112 before extending upwardly to the venturi pump 124.
  • the distance the venturi supply line 140 extends below the cooling chamber 112 is selected to establish a hydraulic pressure head in the venturi supply line 140 which can then support the pressurised evaporation of the cooling fluid 120, for example liquid nitrogen, in the upwardly extending portion of the venturi supply line 140 to create a pressurised flow of gaseous nitrogen (or other cryogen) to be driven through the venturi pump 124.
  • the pressure head can also act to prevent backflow of the cooling fluid 120 in the venturi supply line 140.
  • a check valve (not shown) and/or expansion valve (not shown) may be provided in the venturi supply line 140, for example along the lowermost section thereof, to facilitate the phase change from liquid to gaseous cryogen.
  • the thermal design of the venturi supply line 140 may be such as to effect controlled evaporation and pressurisation of the gaseous cryogen in order to drive the venturi pump 124. Further optionally heating elements (not shown) may be employed to effect vaporisation of the liquid cryogen in the venturi supply line 140.
  • This flow of gaseous cryogen is then the driving fluid of the venturi pump 124 which can be utilised to reduce the pressure in the cooling chamber 112 by means of a suction line 130 connected between a throat of the venturi pump 124 and a headspace 132 of the cooling chamber 112.
  • FIG. 3 there is illustrated a third embodiment of a cryogen cooling system, generally indicated as 210, again for use in electrical power transmission or cryogen transport.
  • like components have been accorded like reference numerals and unless otherwise stated perform a like function.
  • the cooling system 210 comprises a cryostat C defining a fluid flow path for a liquid cryogen, a cooling chamber 212 into which extends a supply line 214 and out of which runs a return line 216, with a cooling element 218 connected therebetween within the interior space of the cooling chamber 212.
  • the cooling element 218 is in the form of a coiled or corrugated tube of thermally conductive material, the cooling chamber 212 being filled with a cooling fluid 220 to immerse the cooling element 218.
  • a fill line 222 is provided between the supply line 214 and the cooling chamber 212 in order to allow the level of the cooling fluid 220 to be maintained despite evaporation during use.
  • the cryogen cooling system 210 further comprises a venturi pump 224 having an inlet 226 being connected via a venturi supply line 240 to the supply line 214 such that the cryogen from the cable cryostat C is used directly as the source of driving fluid for the venturi pump 224.
  • the liquid cryogen is then allowed to evaporate to create a pressurised flow of gaseous nitrogen (or other cryogen) to be driven through the venturi pump 224.
  • An expansion valve (not shown) may be provided in the venturi supply line 240 to facilitate this phase change from liquid to gaseous cryogen. This flow of gaseous cryogen is then the driving fluid of the venturi pump 224.
  • thermoelectric devices such as a peltier cell may be employed to generate local electrical power based on a temperature differential which may be established using the reduced temperatures of the cryogenic fluids employed.
  • the cryogen cooling system 310 comprises a cryostat C for an elongate superconducting cable including superconducting material cooled by a cryogen conveyed alongside or surrounding the superconducting material in the cryostat C.
  • the cooling system 310 further comprises a cooling chamber 312 and directly through which the cryostat C extends unlike in the previous embodiments.
  • the cryostat C comprises an evaporator 318 on that portion of the cryostat C contained within the interior space of the cooling chamber 312. The cryostat C thus solely defines the fluid flow path for conveying cryogen through the cooling chamber 312.
  • the evaporator 318 differs from the previous embodiments by facilitating fluid transfer in the form of evaporation of a portion of the cryogen flowing through the cryostat C within the interior volume of the cooling chamber 312 in order to effect cooling of the remaining liquid cryogen in the catheter C via the latent heat of vaporisation.
  • the interior volume of the cooling chamber 312 is not filled with a cooling fluid in order to allow this evaporation to take place.
  • the evaporator 318 is in the form of a tube of porous or wick like material forming an outer wall of the cryostat C and across which a portion of the liquid cryogen will migrate.
  • the cryogen cooling system 310 comprises a venturi pump 324 having an inlet 326 being connected via a venturi supply line 340 to the cryostat C such that the cryogen from the cable cryostat C is used as the source of driving fluid for the venturi pump 324 as hereinbefore described.
  • the venturi supply line 340 is adapted to effect the evaporation of the liquid cryogen so as to create a pressurised flow of gaseous cryogen to be driven through the venturi pump 324.
  • An expansion valve (not shown) may be provided in the venturi supply line 340 to facilitate this evaporation. This flow of gaseous cryogen is then the driving fluid of the venturi pump 324.
  • the venturi supply line 340 may be extended below the cryostat C before extending upwardly to the venturi pump 324 in order to establish a hydraulic pressure head in the venturi supply line 340 which can then support the pressurised evaporation of the cryogen in portion of the venturi supply line 340 above the cryostat so as to create a pressurised flow of gaseous cryogen to be driven through the venturi pump 324.
  • a check valve (not shown) and/or expansion valve (not shown) may be provided in the venturi supply line 340 to facilitate the phase change from liquid to gaseous cryogen.
  • the venturi pump 324 is connected to the cooling chamber 312 via a suction line 330 in order to allow the pressure reduction in the cooling chamber 312 to be established which then drives evaporation and thus cooling of the cryogen flowing through the evaporator 318.
  • cryogen cooling system 410 for use in electrical power transmission or the like.
  • the cryogen cooling system 410 comprises an elongate cryostat C which may include superconducting material cooled by a cryogen conveyed alongside or surrounding the superconducting material in said cryostat C.
  • the cooling system 410 further comprises a cooling chamber 412 through which the cryostat C directly extends, an evaporator 418 being provided on that portion of the cryostat C contained within the interior space of the cooling chamber 412.
  • the evaporator 418 is similar in function to the fourth embodiment, facilitating fluid transfer in the form of evaporation of a portion of the cryogen flowing through the cryostat C within the interior volume of the cooling chamber 412 in order to effect cooling of the remaining liquid cryogen via the latent heat of vaporisation.
  • the evaporator 418 is in the form of a tube or wall of the cryostat C incorporating a plurality of nozzles (not shown) which may be provided on or formed integrally with the tube.
  • the nozzles (not shown) are configured to effect evaporation of the cryogen in response to passage through the nozzles in combination with a low pressure environment within the cooling chamber 412.
  • Low pressure within the cooling chamber 412 is established by a venturi pump 424 having an inlet 426 being connected via a venturi supply line 440 to the cryostat C as hereinbefore described.
  • the venturi pump 424 is connected to the cooling chamber 412 via a suction line 430 in order to allow the pressure reduction in the cooling chamber 412 to be established which then drives evaporation through the nozzles (not shown) and thus cooling of the cryogen flowing through the evaporator 418.
  • FIG. 6 there is illustrated a sixth embodiment of a cryogen cooling system, generally indicated as 510.
  • the cryogen cooling system 510 again comprises an elongate cryostat C which including superconducting material cooled by a cryogen conveyed alongside or surrounding the superconducting material in a cryostat C or may simply transport the cooled cryogen for alternative applications as hereinbefore described.
  • the cryogen cooling system 510 further comprises a cooling chamber 512 into which the cryostat C extends directly and which is in open fluid communication with an interior of the cooling chamber 512 and thus unlike previous embodiments the supply feeds the cryogen directly into the interior of the cooling chamber 512 to mix with a reservoir of cooling fluid 520 located therein.
  • the portion of the cryostat C entering the cooling chamber 512 is therefore only in fluid communication with the opposed portion of the cryostat C exiting the cooling chamber 512 by means of the interior volume of the cooling chamber 512 and the cooling fluid 520 therein. There is no cooling or evaporating element within the cooling chamber 512 as with all previous embodiments.
  • the cooling fluid 520 is therefore used as a reservoir into which the warm cryogen from the cryostat C is fed and a reservoir from which cooled cryogen is fed into the exiting portion of the cryostat C.
  • the pressure in the cooling chamber 512 is maintained at a level low enough to effect evaporative cooling of the cooling fluid 520.
  • This reduced pressure is produced by means of a venturi pump 524 having an inlet 526 being connected via a venturi supply line 540 to the cryostat C such that the cryogen from the cryostat C is used as the source of driving fluid for the venturi pump 524 as described with reference to previous embodiments.
  • the venturi supply line 540 is adapted to effect the evaporation of the liquid cryogen so as to create a pressurised flow of gaseous cryogen to be driven through the venturi pump 524.
  • the venturi pump 524 is connected at a headspace 532 of the cooling chamber 512 via a suction line 530 in order to allow the pressure reduction in the cooling chamber 512 to be established to drives evaporation and thus cooling of the cooling fluid 520.
  • the pressure in the cooling chamber 512 may be at 200mbar, and as a result the pressure in the cryostat C, at least directly upstream of the cooling chamber 512, should be reduced to match or closely approximate the pressure in the cooling chamber 512.
  • Any suitable pressure metering device (not shown) may be provided on the supply cryostat C in order to achieve the necessary pressure change.
  • FIG. 7 there is illustrated a seventh embodiment of a cryogen cooling system, generally indicated as 610, for use in electrical power transmission or liquid cryogen transport.
  • a cryogen cooling system for use in electrical power transmission or liquid cryogen transport.
  • like components have been accorded like reference numerals and unless otherwise stated perform a like function.
  • the cryogen cooling system 610 is a modified arrangement of the cooling system 110 of the second embodiment illustrated in Figure 2 .
  • the cooling system 610 again comprises a cryostat C conveying a liquid cryogen to be cooled, a cooling chamber 612 through which a fluid flow path comprising the cryostat C extends, and a venturi pump 624 to effect reduced pressure and therefore temperature within the cooling chamber 612 as hereinbefore described.
  • the venturi pump 624 is fed via a venturi supply line 640 which is supplied directly from the cooling chamber 612 which applies a pressure head within the venturi supply line 640.
  • a venturi supply line 640 Located on the venturi supply line 640 upstream of the venturi pump 624 is a fluid powered motor 650 through which the liquid cryogen flows, under pressure, in order to drive the motor 650 and produce electrical power which can be utilised by the cooling system 10.
  • a source of local electrical power can be generated for use as required by the cooling system 10.
  • Additional or alternative expansion valves may be provided between the motor 650 and venturi pump 624 in order to ensure the correct phase and pressure are achieved to efficiently drive the venturi pump 624.
  • This motor arrangement may be implemented on any of the embodiments of Figures 2 to 6 which incorporate a venturi supply line which is locally supplied with cryogen.
  • cryogen cooling systems 10; 110; 210; 310; 41; 510; 610 of the invention allow for localised cooling of the cryogen flowing through the cryostat C, and by means of a venturi pump 24; 124; 224; 324; 424; 524; 624 which avoids the need for a conventional vacuum pump.
  • Such conventional vacuum pumps employ high speed drive shafts/rotors, seals, and other moving parts that can wear and thus reduce performance.
  • any reduction in performance of such a crucial component which would lead to a reduction in the cooling performance and therefore an unacceptable increase in the temperature of the superconducting material, can lead to catastrophic failure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
EP23187129.4A 2023-07-21 2023-07-21 Kryogenkühlsystem Withdrawn EP4495511A1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP23187129.4A EP4495511A1 (de) 2023-07-21 2023-07-21 Kryogenkühlsystem
PCT/EP2024/070611 WO2025021707A1 (en) 2023-07-21 2024-07-19 A cryogen cooling system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP23187129.4A EP4495511A1 (de) 2023-07-21 2023-07-21 Kryogenkühlsystem

Publications (1)

Publication Number Publication Date
EP4495511A1 true EP4495511A1 (de) 2025-01-22

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EP23187129.4A Withdrawn EP4495511A1 (de) 2023-07-21 2023-07-21 Kryogenkühlsystem

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EP (1) EP4495511A1 (de)
WO (1) WO2025021707A1 (de)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6145321A (en) * 1998-07-13 2000-11-14 Air Products And Chemicals, Inc. Method and apparatus for cooling an aqueous liquid
US6164078A (en) * 1999-03-04 2000-12-26 Boeing North American Inc. Cryogenic liquid heat exchanger system with fluid ejector
JP2003307375A (ja) * 2002-04-15 2003-10-31 Air Liquide Japan Ltd 冷却装置及び冷却方法
DE102017003105A1 (de) * 2017-03-30 2018-10-04 Linde Aktiengesellschaft Verfahren und Vorrichtung zum Kühlen eines Bauteils

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6145321A (en) * 1998-07-13 2000-11-14 Air Products And Chemicals, Inc. Method and apparatus for cooling an aqueous liquid
US6164078A (en) * 1999-03-04 2000-12-26 Boeing North American Inc. Cryogenic liquid heat exchanger system with fluid ejector
JP2003307375A (ja) * 2002-04-15 2003-10-31 Air Liquide Japan Ltd 冷却装置及び冷却方法
DE102017003105A1 (de) * 2017-03-30 2018-10-04 Linde Aktiengesellschaft Verfahren und Vorrichtung zum Kühlen eines Bauteils

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