EP4607128A2 - System und verfahren zur bereitstellung von kryogener kühlung - Google Patents

System und verfahren zur bereitstellung von kryogener kühlung

Info

Publication number
EP4607128A2
EP4607128A2 EP25188742.8A EP25188742A EP4607128A2 EP 4607128 A2 EP4607128 A2 EP 4607128A2 EP 25188742 A EP25188742 A EP 25188742A EP 4607128 A2 EP4607128 A2 EP 4607128A2
Authority
EP
European Patent Office
Prior art keywords
nitrogen
refrigeration
liquid
turbine
refrigeration system
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.)
Pending
Application number
EP25188742.8A
Other languages
English (en)
French (fr)
Other versions
EP4607128A3 (de
Inventor
Neil M. Prosser
James R. Handley
Ricardo Dutra DE CASTRO COSTA
John F. Billingham
David R. Parsnick
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.)
Praxair Technology Inc
Original Assignee
Praxair Technology 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 Praxair Technology Inc filed Critical Praxair Technology Inc
Publication of EP4607128A2 publication Critical patent/EP4607128A2/de
Publication of EP4607128A3 publication Critical patent/EP4607128A3/de
Pending legal-status Critical Current

Links

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
    • F25B9/002—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
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/004—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being air
    • 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
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0012—Primary atmospheric gases, e.g. air
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0012—Primary atmospheric gases, e.g. air
    • F25J1/0015—Nitrogen
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0035—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work
    • F25J1/0037—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work of a return stream
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/004—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by flash gas recovery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0042—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by liquid expansion with extraction of work
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0045—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by vaporising a liquid return stream
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/005—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by expansion of a gaseous refrigerant stream with extraction of work
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/0052—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/0052—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream
    • F25J1/0057—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream after expansion of the liquid refrigerant stream with extraction of work
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
    • F25J1/007—Primary atmospheric gases, mixtures thereof
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
    • F25J1/007—Primary atmospheric gases, mixtures thereof
    • F25J1/0072—Nitrogen
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0201—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using only internal refrigeration means, i.e. without external refrigeration
    • F25J1/0202—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using only internal refrigeration means, i.e. without external refrigeration in a quasi-closed internal refrigeration loop
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0203—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a single-component refrigerant [SCR] fluid in a closed vapor compression cycle
    • F25J1/0204—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a single-component refrigerant [SCR] fluid in a closed vapor compression cycle as a single flow SCR 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0228—Coupling of the liquefaction unit to other units or processes, so-called integrated processes
    • F25J1/0235—Heat exchange integration
    • F25J1/0236—Heat exchange integration providing refrigeration for different processes treating not the same feed stream
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    • F25J1/0237—Heat exchange integration integrating refrigeration provided for liquefaction and purification/treatment of the gas to be liquefied, e.g. heavy hydrocarbon removal from natural gas
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    • F25J1/0262—Details of the cold heat exchange system
    • F25J1/0264—Arrangement of heat exchanger cores in parallel with different functions, e.g. different cooling streams
    • F25J1/0265—Arrangement of heat exchanger cores in parallel with different functions, e.g. different cooling streams comprising cores associated exclusively with the cooling of a refrigerant stream, e.g. for auto-refrigeration or economizer
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    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0285—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings
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    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0292—Refrigerant compression by cold or cryogenic suction of the refrigerant 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0294—Multiple compressor casings/strings in parallel, e.g. split arrangement
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2205/00—Processes or apparatus using other separation and/or other processing means
    • F25J2205/02—Processes or apparatus using other separation and/or other processing means using simple phase separation in a vessel or drum
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2210/00—Processes characterised by the type or other details of the feed stream
    • F25J2210/40—Air or oxygen enriched air, i.e. generally less than 30mol% of O2
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2210/00—Processes characterised by the type or other details of the feed stream
    • F25J2210/42—Nitrogen
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2220/00—Processes or apparatus involving steps for the removal of impurities
    • F25J2220/02—Separating impurities in general from the feed stream
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/08—Cold compressor, i.e. suction of the gas at cryogenic temperature and generally without afterstage-cooler
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/24—Multiple compressors or compressor stages in parallel
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/30—Compression of the feed stream
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2240/00—Processes or apparatus involving steps for expanding of process streams
    • F25J2240/40—Expansion without extracting work, i.e. isenthalpic throttling, e.g. JT valve, regulating valve or venturi, or isentropic nozzle, e.g. Laval
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/02—Bath type boiler-condenser using thermo-siphon effect, e.g. with natural or forced circulation or pool boiling, i.e. core-in-kettle heat exchanger
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/04—Internal refrigeration with work-producing gas expansion loop
    • F25J2270/06—Internal refrigeration with work-producing gas expansion loop with multiple gas expansion loops
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/14—External refrigeration with work-producing gas expansion loop
    • F25J2270/16—External refrigeration with work-producing gas expansion loop with mutliple gas expansion loops of the same 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/12—Particular process parameters like pressure, temperature, ratios

Definitions

  • cryogenic refrigeration systems tailored for supercomputing applications, such as quantum computing operations performed at large data centers.
  • Quantum computer memory and processing requirements must be operated at cryogenic temperatures, which often require the refrigeration to be supplied at or near liquid nitrogen temperatures.
  • the present invention may be broadly characterized as a liquid nitrogen based refrigeration system integrated with a refrigeration load circuit and associated methods comprising: (1) a nitrogen refrigerator having one or more recycle compressors, a warm booster compressor, a cold booster compressor, a warm turbine, a cold turbine, and a heat exchanger with at least one cooling passage and at least one recycle passage; and (2) a refrigeration load circuit having an expansion valve or a liquid turbine; a separator, a buffer tank, and a refrigeration load.
  • the nitrogen refrigerator is configured to receive a source of nitrogen gas as well as a cold nitrogen gas return stream and produce a liquid nitrogen refrigerant stream.
  • the refrigeration load circuit is configured to: (a) receive the nitrogen refrigerant stream; (b) expand the nitrogen refrigerant stream in the expansion valve or the liquid turbine; (c) separate the expanded nitrogen refrigerant stream in the separator into liquid and vapor portions; (d) cool a refrigeration load with the liquid portion of the expanded nitrogen refrigerant stream while vaporizing the liquid portion of the expanded refrigerant stream; and (e) return the vaporized stream and the vapor portion of the nitrogen refrigerant stream as the nitrogen return stream to the nitrogen refrigerator.
  • the present integrated liquid nitrogen based refrigeration system and associated methods may include various optional elements and advantages features as generally shown and described below with reference to the embodiments illustrated in Figs. 1-5 and 8-10 of the accompanying drawings. Incorporation of one or more of the preferred optional elements and advantages features very much depend on the cooling requirements of the refrigeration load including the target refrigeration temperature and operating pressures of the refrigeration system.
  • the present invention may also be broadly characterized as a closed loop liquid nitrogen based refrigerator comprising: (1) a recycle compressor; (2) a cold booster compressor; (3) a cold turbine; (4) a primary heat exchanger with at least one cooling passage and at least one recycle passage; and (5) an auxiliary heat exchanger to cool a separate refrigerant in a closed-loop refrigeration load circuit in via indirect heat exchange between liquid nitrogen in the refrigerator and the separate refrigerant in a closed-loop refrigeration load circuit.
  • the closed loop liquid nitrogen based refrigerator and associated methods may include elements and features as generally shown and described below with reference to the embodiments illustrated in Figs. 6-7 of the accompanying drawings.
  • cryogenic refrigeration system may be configured as a closed loop refrigeration arrangement (See Figs. 6-7 ).
  • a common and key feature is the scalability of the depicted system wherein the systems can be sized to provide from as low as about 20kW of refrigeration to 2000 kW of refrigeration or more.
  • the specific configuration or arrangement of the nitrogen refrigerator can be optimized depending on the temperature requirements needed to cool the refrigeration load in the supercomputing application or other cryogenic refrigeration applications.
  • Fig. 1 there is shown a simplified schematic of the present system and method for supplying cryogenic refrigeration to a refrigeration load in supercomputing applications.
  • the illustrated system is a liquid nitrogen based refrigeration system 10 integrated with the end-use application (i.e. refrigeration load) 20 and includes a heat exchanger 12, recycle compressor(s) 14, turboexpander(s) 16, and a return gas circuit 18.
  • the specific arrangement of the nitrogen refrigerator (i.e. heat exchanger 12, recycle compressor(s) 14, and turboexpander(s) 16) as well as the return gas circuit 18 is highly dependent on the temperature requirements needed to cool the refrigeration load 20, which in turn dictates the operating pressures of the nitrogen refrigerator 10.
  • the most efficient and most cost effective manner of providing the cryogenic refrigeration would be to configure the integrated liquid nitrogen based refrigerator to supply nitrogen refrigerant at minimum achievable temperature.
  • the minimum achievable temperature is typically tied to the pressure of the liquid nitrogen in the refrigeration loop, and which is preferably attained by reducing the pressure of the in the cryogenic refrigeration loop to at or near ambient pressure.
  • ambient pressure i.e. about 14.7 psia
  • the liquid nitrogen is at a temperature of about 77.3 K, which is generally the minimum available temperature for a nitrogen refrigerator that is configured to operate at ambient or higher pressures. Operation of a nitrogen refrigerator at sub-ambient pressures is not practical nor desired as the potential for air in-leakage could lead to freezing of any moisture, carbon dioxide, and other air contaminants which could lead to failure or underperformance of the nitrogen refrigerator.
  • the nitrogen refrigeration system must be controlled so that the temperature of the vaporized nitrogen exiting the refrigerator is the minimum available temperature which, as indicated above, occurs when the liquid nitrogen is at or near ambient pressure.
  • a cold compressor 19 is optionally used.
  • the nitrogen refrigerator produces cold liquid nitrogen at high pressure.
  • the most efficient nitrogen refrigerator design would provide the cold nitrogen at high pressures, and in some applications the nitrogen is supplied at or above the critical pressure. For refrigeration supply temperatures of between about 77.5 K to 79.1 K the nitrogen pressure exiting the refrigeration load is between about 15 psia to about 18 psia.
  • cryogenic refrigeration at temperatures of about 80.1 K is acceptable for the intended application
  • the pressure can be about 20 psia. In this case, or in similar applications where the temperature nitrogen refrigeration supply can be even warmer, the vaporized nitrogen can be returned to the nitrogen refrigerator without a cold compressor.
  • the nitrogen stream returning or recycling back to the nitrogen refrigerator is at its lowest pressure at the warm end of the heat exchanger just before it enters the recycle compressor(s).
  • this recycled nitrogen stream should be at or more preferably above atmospheric pressure in order to avoid the possibility of air in-leakage, as this would lead to freezing in the nitrogen refrigerator, and possibly create operational problems in the refrigeration load system.
  • the optional cold blowers raise the pressure of the vaporized nitrogen as it exits the refrigeration load system such that the return circuit pressure to ensure maintained above atmospheric pressure. Depending on the intended application, multiple, redundant cold blowers may be required to achieve a high reliability often required of cryogenic refrigeration systems.
  • Table 1 shows the approximate power consumption to provide refrigeration with cryogenic liquid at varying design temperatures based on computer based simulations and models. The relationship between temperature and pressure exiting the refrigeration load is shown in Table 1.
  • the relative refrigerator power demand i.e. relative power consumption
  • the nitrogen refrigerant approaches its critical point, its latent heat begins to decrease rapidly. Note that the critical point temperature of nitrogen is 126.2 K and its corresponding critical point pressure is 493 psia.
  • the liquid nitrogen is passed from the separator 140 to a buffer tank 150, which directly supplies the liquid nitrogen refrigerant to the refrigeration load 120.
  • the liquid nitrogen level in the buffer tank is controlled to balance the refrigeration load 120. This control is preferably adjusted by adjusting the nitrogen refrigerant production of the refrigerator system 100.
  • the return stream 122 from the refrigeration load 120 is saturated vapor or slightly superheated nitrogen vapor.
  • the optional cold compressor 119 is needed only when the refrigeration supply temperature is required to be near its minimum available temperature, between about 77.5 K to about 79.1 K.
  • the return stream 122 from the refrigeration load 120 is combined with the nitrogen vapor 152 from the separator 150 and introduced into a low pressure return circuit 123 ( Figs.
  • An optional liquid storage tank 160 is also shown in the various embodiments including those embodiments shown in Figs. 2-5 .
  • the purpose of the optional liquid storage tank 160 is to hold externally supplied liquid nitrogen or to hold liquid nitrogen produced from the liquefier of the nitrogen refrigerator.
  • liquid nitrogen could be produced by the nitrogen refrigerator in a modal operating method that produces excess liquid nitrogen part of the time and/or consumes the stored liquid nitrogen part of the time. This modal operating method may be advantageous in situations where power costs vary as a function of time.
  • excess liquid nitrogen could be produced by the nitrogen refrigerator for export as a merchant liquid or for other uses at the customer site in addition to meeting the cooling requirements of the intended application.
  • a modal operating method for excess liquid nitrogen production and/or liquid nitrogen consumption may require substantial gas storage at the warm end of the cryogenic refrigeration system.
  • a plurality of gas receivers See e.g. Fig. 9 ) would be configured to store nitrogen molecules when the liquid nitrogen tank is emptying; and the gas receivers would supply the nitrogen molecules when the liquid nitrogen tank is filling.
  • a nitrogen producing air separation unit See e.g. Fig. 10 ) may be required, particularly during modal operation when the gas receiver volume or capacity could become impractically or uneconomically large.
  • the radial inflow turbines 170, 175 used in the illustrated embodiments are capable of high efficiency without compromising operating rangeability and are configured to operate at a pressure ratio of between about 8.5 to 10.0.
  • the nitrogen stream exiting the cold turbine 175 must be lower than about 90 psia and more preferably between 80 psia and 90 psia.
  • the nitrogen stream exiting the turbine is nearly a saturated vapor or it can be up to 10% liquid or even several degrees superheated.
  • the high pressure feed stream 178 is approximately 800 psia.
  • This high pressure feed stream 178 enhances the efficiency of the refrigeration system 100 for two thermodynamically based reasons.
  • the higher pressure stream results in a straighter cooling curve. As its pressure gets higher above the nitrogen critical pressure of 493 psia, the change in heat capacity as it cools is reduced, resulting in less severe "kinks" in the cooling curve. In the lower direction, as its pressure becomes subcritical, the cooling curve then has a constant temperature latent heat zone which creates a very uneven cooling curve and is very thermodynamically irreversible.
  • Second, higher pressure streams to the turbine are beneficial thermodynamically simply because they have higher heat capacities. This simply means they are better able to recover refrigeration with lower flows, which results in lower flow and power consumption in the recycle compressors.
  • both the warm turbine 170 and the cold turbine 175 operate at similar pressures.
  • the warm turbine flow is typically about one-half of the cold turbine flow for this cycle.
  • the refrigeration demand for the warm turbine is comparatively lower.
  • the warm turbine flow in the embodiment of Fig. 2 is preferably only between about 10% to about 20% of the cold turbine flow. Because of this reduced warm turbine flow, elimination of the warm turbine and booster may even be considered or contemplated for this embodiment.
  • the discharge stream 115 from the medium pressure recycle compressor 114 is fed to the warm booster 172 and cold booster 176 in parallel, and their respective discharge streams 173 and 177 are recombined to form combined stream 178 at the highest pressure in the cycle before they enter the heat exchanger 112, which is preferably a brazed aluminum heat exchanger.
  • the low pressure recycle compressor 113 raises the pressure of the combined feed stream made up of the warmed low pressure flash gas stream 144 and return stream 145 from the refrigeration load 120.
  • a small make-up flow 111 may be required to compensate for leakage losses in the turbomachinery. Very low leakage seals, such as dry gas seals, can be employed if desired to minimize this flow.
  • the target refrigeration temperature is preferably about 95 K to about 97 K.
  • the pressure from gas return stream 145 exiting the refrigeration load circuit is as high as the pressure in the exhaust stream from the cold turbine 175.
  • the embodiment of Fig. 3 has no low pressure gas return stream and no low pressure recycle compressor.
  • FIG.4 Yet another embodiment and refrigeration cycle is shown in Fig.4 .
  • the feed nitrogen 136 to the warm turbine 170 is piped from the recycle compressor discharge 115 rather than the warm and cold booster streams.
  • the warm booster 172 and cold booster 176 operate in series rather than parallel, with a portion of the recycle compressor discharge shown as stream 138 first compressed in the warm booster 172, then in the cold booster 176.
  • the high pressure stream 178 from the cold booster discharge supplies the cold turbine 175 and the cold liquid nitrogen product stream exiting passage 129 at the cold end of the heat exchanger 112.
  • Fig. 5 shows yet another alternative embodiment of the cryogenic refrigerator having a liquefaction cycle that provides improved efficiency compared to conventional liquefaction systems.
  • the warm turbine inlet and the cooling product are designed to operate at a very high pressure such as about 1300 psia, although the optimum operating pressure likely depends on the heat exchanger 112 and turbomachinery design tradeoffs.
  • the higher pressure within the liquefaction cycle improves the thermodynamic efficiency of the nitrogen refrigerator by improving the reversibility of the heat exchanger temperature profile and because of the higher heat capacity of the feed streams.
  • the cold turbine 175 must operate with an exhaust pressure approximately the same as it is for other liquefiers, so that it is sufficiently cold to cool the liquid nitrogen product stream exiting passage 129 at the cold end of the heat exchanger 112 to the desired target refrigeration temperature.
  • the cold turbine 175 must have a lower pressure feed and preferably the lower pressure feed 136 is supplied as a portion from the discharge stream 115 from high pressure recycle compressor 114.
  • the warm turbine exhaust in the embodiment of Fig. 5 is supplied to a separate, intermediate pressure circuit 124 or passage within the heat exchanger 112. This feature provides some design freedom in selecting the desired exhaust pressure of the warm turbine 170, and the corresponding return pressure between the medium pressure recycle compressors 113A, 113B and the high pressure recycle compressor 114.
  • the warm booster 172 and cold booster 176 are fed in series, albeit in reverse order, with the portion of feed stream 138 first directed to the cold booster 176 and subsequently directed to the warm booster 172.
  • the additional heat exchange zone, shown as X-2 is preferably disposed between the warm turbine exhaust and cold turbine draw in a manner similar to that of the nitrogen refrigerator of Fig. 4 .
  • a closed loop refrigeration concept such as that shown in Figs. 6-7 should be used.
  • a separate refrigeration circuit 202 containing an alternate refrigerant is used to cool the refrigeration load 220.
  • a closed loop nitrogen based refrigerator 205 is used to generate the refrigeration that is indirectly transferred to the separate refrigeration load circuit 202. This is done using vapor nitrogen exiting the turboexpander 216, which is passed through an auxiliary heat exchanger 215 to cool the alternate refrigerant in separate refrigerant circuit 202.
  • the alternate refrigerant fluid is selected such that it provides constant temperature refrigeration using its latent heat.
  • the preferred alternate refrigerant(s) will have its normal boiling point slightly below the target refrigeration temperature so that the separate refrigeration circuit pressure is modestly above ambient pressure, avoiding concerns for air in-leakage.
  • the critical temperature of the alternate refrigerant must be higher than the target refrigeration temperature, preferably by a large margin. Circulating the alternate refrigerant at temperatures well below the critical temperature means the refrigeration circuit can be operated at a moderate pressure, and the flow rate within the refrigeration circuit would be relatively low.
  • the preferred alternate refrigerant is non-toxic and inflammable. It is also desirable that the alternate refrigerant has the lowest possible greenhouse warming potential. Potential alternate refrigerants and the normal boiling points include: Krypton (119.9 K); R-14 (145.4 K); nitrous oxide (184.7 K); R-23 (191.1 K); R-41 (195.0 K); and R-116 (195.0 K).
  • Fig. 6 shows a simplified schematic of the closed loop liquid nitrogen based refrigeration system 200 that includes a main heat exchanger 212, an auxiliary heat exchanger 215, recycle compressor(s) 214, and turbine(s) 216, and as well as the associated gas circuits.
  • the separate alternate refrigerant based system 202 is also a closed loop refrigeration system incorporating the auxiliary heat exchanger 215, one or more pumps 217, and the refrigeration load 220.
  • the pump 217 is used raise the pressure of the alternate refrigerant after it is condensed in the auxiliary heat exchanger 215 so that it can be recirculated.
  • a pump is preferred instead of a gas phase blower because the pump is generally lower cost, requires less power, and generally causes less of a thermodynamic penalty.
  • multiple pumps may be employed.
  • the gas nitrogen exiting the turboexpander (i.e. turbine) 216 is the lowest temperature stream in the refrigerator. It directly provides the refrigeration to balance the refrigerant circuit.
  • the flow of the turbine exhaust stream in the liquid nitrogen based refrigerator must be sufficiently high and the temperature must be sufficiently cold to provide the necessary cooling in the auxiliary heat exchanger 215.
  • the auxiliary heat exchanger 215 is preferably a counter-current heat exchanger that exhibits a large temperature difference at its cold end, where the turbine exhaust stream enters the auxiliary heat exchanger 215.
  • the temperature difference of the counter flowing streams in the auxiliary heat exchanger 215 progressively decreases and is tightest at the auxiliary heat exchanger warm end, where the turbine exhaust stream exits the auxiliary heat exchanger 215. So, the temperature of the turbine exhaust stream exiting the warm end of the heat exchanger limits the operating temperatures of the refrigeration system 200.
  • FIG. 7 A more detailed embodiment of the closed-loop nitrogen refrigerator is shown in Fig. 7 .
  • the cold turbine 216 supplies sufficient refrigeration so there is generally no need for a warm turbine.
  • the turbine exhaust temperature and flow are optimized to achieve the lowest power and capital solution. Reduction in cold turbine flow means that the cold turbine exhaust temperature must also be reduced in order to provide the refrigeration demand.
  • the lowest power solution will have a small temperature difference at the warm end of the heat exchanger 212, which indicates minimized wasted refrigeration.
  • the selection of pressure levels is very unconstrained, since there is no liquid generated in the refrigerator 205. As for the other systems, higher pressures will tend to improve efficiency. Also, the turbine pressure ratio should not exceed 8.5-10.0.
  • a turbine pressure ratio lower than about 10.0 yields a significant power savings.
  • the lower pressure ratio requires increased flow, which gives a more uniform cooling curve in the heat exchanger 212 and improved efficiency (reduces the temperature difference at the cold end).
  • the pressure levels are decreased.
  • the pressures of the recycle compressor and the turbine are decreased such that the pressure ratio across each are held constant and the volumetric flows are also constant.
  • the recycle compressor 214A, 214B and turbine 216 each maintain their design aerodynamic efficiencies.
  • a plurality of aftercoolers 279 may be employed downstream of compressors and a small make-up flow 211 may be required to compensate for leakage losses in the turbomachinery.
  • the cold turbine exhaust pressure is maintained well above atmospheric pressure.
  • the lowest pressure of the system 200 will remain above atmospheric at turndown.
  • a liquid buffer tank, or multiple tanks will probably be needed for control and operation of the refrigerant circuit.
  • the refrigeration output of the present system and method is primarily be controlled by modulating the refrigerant flow rate and the nitrogen refrigerator should be modulated to balance the refrigeration load.
  • the most efficient turndown method of the nitrogen refrigerator is preferably the same as turndown in nitrogen liquefiers. During such turndowns, all the pressure levels within the liquefier/refrigerator fall in concert so that the turbines and the recycle compressor pressure ratios and volumetric flow rates stay nearly constant. In this way these turbomachines continue to operate at or near their design point efficiencies.
  • This turndown method also enables a very large turndown range. Generally, the turbine inlet nozzle positions are fixed in this method. The pressure at the suction of the low pressure recycle compressor will necessarily decrease when turndown is affected using this method.
  • Fig. 9 shows an example refrigeration configuration similar to the embodiment of Fig. 2 but with an optional throttle valve 345 disposed in the low pressure return circuit 123 near the cold end of the heat exchanger 112 that would be used if the turndown method allowed the low pressure recycle compressor suction pressure to decrease.
  • Us e of the optional throttle valve 345 keeps the refrigeration load circuit at constant pressure and refrigeration temperature, rather than allowing it to fall with the pressure of the low pressure recycle compressor 113. Locating this optional throttle valve 345 at the cold end of the heat exchanger 112 is thermodynamically better than locating the throttle valve at the warm end of the heat exchanger 112. However, the optional throttle valve 345 and installation thereof is generally less costly if it is configured or located at the warm end.
  • the buffer tank may be used for liquid nitrogen addition or liquid nitrogen manufacture in lieu of a separate storage tank.
  • the buffer tank would probably be sized larger to satisfy the dual functions.
  • Another contemplated variant would be to combine the separator and buffer tank function in a single liquid vessel.
  • Some further contemplated alternatives include arrangements where the optional liquid turbine is loaded by a compressor that raises the pressure of another stream or it could be loaded by an energy dissipating brake instead of loading by a generator.
  • the optional liquid turbine is a power saving feature that may be used in applications where the additional capital costs are justified.

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  • Engineering & Computer Science (AREA)
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EP25188742.8A 2019-12-19 2020-12-01 System und verfahren zur bereitstellung von kryogener kühlung Pending EP4607128A3 (de)

Applications Claiming Priority (3)

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US201962950198P 2019-12-19 2019-12-19
PCT/US2020/062665 WO2021126513A1 (en) 2019-12-19 2020-12-01 System and method for supplying cryogenic refrigeration
EP20828810.0A EP4078047A1 (de) 2019-12-19 2020-12-01 Systeme und verfahren für tieftemperaturkühlung

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EP4537034A1 (de) * 2022-06-06 2025-04-16 Chart Energy & Chemicals, Inc. Kühlsystem und -verfahren für kryogenes gas
US20240019207A1 (en) * 2022-07-18 2024-01-18 Jeremiah J. Rauch System and method for gas liquefication
US20240230220A1 (en) * 2023-01-05 2024-07-11 Brian R. Kromer System and method for combined liquefaction and densification of oxygen
US20240288218A1 (en) * 2023-01-05 2024-08-29 Seth A. Potratz Method for production and supply of a densified liquid oxygen product for space vehicle applications
US20240230218A1 (en) * 2023-01-05 2024-07-11 Sean M. Kelly System and method for densification of liquid oxygen
EP4407266A3 (de) * 2023-01-27 2024-10-30 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Verfahren und vorrichtung zur kühlung eines gases mit einem kältekreislauf
FR3146724B1 (fr) 2023-03-16 2025-04-18 Air Liquide Ossature pour un liquéfacteur d’un gaz
US20250060154A1 (en) * 2023-08-17 2025-02-20 Brian R. Kromer System and Method for Turndown of a Hydrogen Precooling and/or Hydrogen Liquefaction System
US20250060153A1 (en) * 2023-08-17 2025-02-20 Brian R. Kromer System and Method for Precooling a Hydrogen Feed Stream with Concurrent Nitrogen Liquefaction

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EP4607128A3 (de) 2025-11-12
US20220404094A1 (en) 2022-12-22
EP4078047A1 (de) 2022-10-26
WO2021126513A1 (en) 2021-06-24

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