US3657898A - Method and apparatus for producing refrigeration - Google Patents

Method and apparatus for producing refrigeration Download PDF

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Publication number
US3657898A
US3657898A US752998A US3657898DA US3657898A US 3657898 A US3657898 A US 3657898A US 752998 A US752998 A US 752998A US 3657898D A US3657898D A US 3657898DA US 3657898 A US3657898 A US 3657898A
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expansion
expansion turbine
compressor
relatively low
pressurized gas
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US752998A
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Leif A Ness
Edmund P Thomas
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Air Products and Chemicals Inc
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Air Products and Chemicals Inc
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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
    • F25B9/06—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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/06—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially
    • F01D1/08—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially having inward flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/005—Adaptations for refrigeration plants
    • 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
    • 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"
    • F25J1/004—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
    • 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
    • F25J1/0208—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 in combination with an internal quasi-closed refrigeration loop, e.g. with deep flash recycle 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
    • F25J1/0228—Coupling of the liquefaction unit to other units or processes, so-called integrated processes
    • F25J1/0234—Integration with a cryogenic air separation unit
    • 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
    • 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.
    • 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.
    • F25J1/0285—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings
    • F25J1/0288—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings using work extraction by mechanical coupling of compression and expansion of the refrigerant, so-called companders
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04151—Purification and (pre-)cooling of the feed air; recuperative heat-exchange with product streams
    • F25J3/04187—Cooling of the purified feed air by recuperative heat-exchange; Heat-exchange with product streams
    • F25J3/04218—Parallel arrangement of the main heat exchange line in cores having different functions, e.g. in low pressure and high pressure cores
    • F25J3/04224—Cores associated with a liquefaction or refrigeration 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04248—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion
    • F25J3/04278—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion using external refrigeration units, e.g. closed mechanical or regenerative refrigeration units
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04248—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion
    • F25J3/04333—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion using quasi-closed loop internal vapor compression refrigeration cycles, e.g. of intermediate or oxygen enriched (waste-)streams
    • F25J3/04351—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion using quasi-closed loop internal vapor compression refrigeration cycles, e.g. of intermediate or oxygen enriched (waste-)streams of nitrogen
    • F25J3/04357—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion using quasi-closed loop internal vapor compression refrigeration cycles, e.g. of intermediate or oxygen enriched (waste-)streams of nitrogen and comprising a gas work expansion 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04248—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion
    • F25J3/04375—Details relating to the work expansion, e.g. process parameter etc.
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04248—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion
    • F25J3/04375—Details relating to the work expansion, e.g. process parameter etc.
    • F25J3/04381—Details relating to the work expansion, e.g. process parameter etc. using work extraction by mechanical coupling of compression and expansion so-called companders
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04248—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion
    • F25J3/04375—Details relating to the work expansion, e.g. process parameter etc.
    • F25J3/04393—Details relating to the work expansion, e.g. process parameter etc. using multiple or multistage gas work expansion
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04763—Start-up or control of the process; Details of the apparatus used
    • F25J3/04866—Construction and layout of air fractionation equipments, e.g. valves, machines
    • 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
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/20—Integrated compressor and process expander; Gear box arrangement; Multiple compressors on a common shaft
    • 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
    • F25J2240/02—Expansion of a process fluid in a work-extracting turbine (i.e. isentropic expansion), e.g. of the feed 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
    • 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
    • F25J2270/90—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration

Definitions

  • a pair of work expansion turbines operate in parallel relation and at materially different temperature levels; the turbines being fed with pressurized gas at substantially the same pressure and discharge the gas at substantially the same relatively low pressure.
  • the critical speed requirements of each expansion turbine is in no way relieved, as in the process employing expansion turbines operating in series as discussed above, and it has not been possible heretofore to directly utilize at a high order of efficiency the energy developed from both parallel operating expansion turbines to drive the final stage of compression while maintaining high expander efficiency.
  • the present invention provides a novel method and ap' paratus for producing refrigeration employing multiple stages of refrigerant compression and two stages of refrigerant work expansion in which the horsepower developed by the work expansion stages'is utilized to drive the final stage of refrigerant compression.
  • the novel process employs and the novel apparatus includes a novel expander-compressor-expander combination in which both expansion turbines operate at different temperature levels under a substantially equal pressure ratio and at high efficiency and in which the power produced from both expansion turbines is applied directly to the compressor operating as the final compression stage and at a high order of efficiency to-thus usefully employ the total energy output of the expansion turbines within the normal range of efficiency obtained for low temperature machinery.
  • the novel arrangement makes it possible to accomplish a greater percentage of the total work of compression in the final compression stage and more efficient compression of the gaseous refrigerant.
  • FIG. 1 is a diagrammatic presentation of a refrigeration cycle embodying the principles of the present invention
  • FIG. 2 is a diagrammatic view, partly in section, of a novel expander-compressor-expander unit provided by the present invention
  • FIG. 3 is a view in section of a part of the structure shown in FIG. 2;
  • FIG. 4 is a three-dimensional view of another part of the structure shown in FIG. 2.
  • the refrigeration cycle shown in FIG. 1 includes a novel expander-compressor-expander unit 10 which includes a compressor ll of the centrifugal type and centripetal turbine expanders 12 and 13 connected to a common shaft 14 with the compressor 11.
  • the compressor 11 comprises the final compression stage of the refrigeration cycle which also includes a first stage compressor 15, driven by any suitable prime mover 16.
  • the compressor 15 compresses refrigerant gas delivered to its suction inlet by conduit 17 to an intermediate pressure and refrigerant gas at the intermediate pressure is conducted by conduit 18 to the suction inlet of the compressor 11 from which the refrigerant gas is delivered in conduit 19 under rela tively high pressure; the compressors 11 and 15 may be provided with conventional after coolers, not shown.
  • the high pressure refrigerant gas is divided witha first part flowing through passageway 20 of heat exchange device 21 and a second part flowing through passageway 22 of heat exchange device 23.
  • the first part of the high pressure refrigerant gas is cooled to below ambient temperature in the heat exchange device 21 by heat interchange with an auxiliary refrigerant supplied by conduits 24 and then conducted by conduit 25 to the inlet of the turbine expander 12 wherein the refrigerant gas is expanded with the production of external work to a pressure corresponding substantially to the inlet pressure of the compressor 15 with concomitant cooling of the gas.
  • the effluent of the turbine expander 12 is conducted by conduits 26 and 27 for flow through passageway 28 of the heat exchange device 23 and thereby warmed to ambient temperature and then conducted by conduit 29 to the conduit 17 for recycling to the compressor 15.
  • the second part of the high pressure refrigerant gas is cooled upon flowing through the passageway 22 and is then divided with one part of the cooled high pressure refrigerant gas flowing through conduit 30 to the inlet of the turbine expander 13 and with a second part flowing through passageway 31 of the heat exchange device 32.
  • the cooled high pressure refrigerant gas is expanded with work to a pressure slightly above the inlet pressure of the compressor 15 with concomitant further cooling to a relatively low temperature.
  • the effluent of the turbine expander 13 may be utilized to provide refrigeration exter nally of the cycle or refrigeration for the cycle, or both.
  • effluent of the turbine expander 13 may be passed by conduit 33 to conduits 34 and 35, provided with control valves 36 and 37, respectively, for flow through passageways 38 and 39, respectively, of heat exchange device 40, in countercurrent heat interchange with an external :fluid flowing through passageway 41.
  • the warm refrigerant gas leaving the warm end of the passageway 39 is conducted by conduit 42 to the conduit 17 for flow to the inlet of the compressor 15, while the refrigerant gas leaving the passageway 38 at a lower temperature is conducted by conduit 43 to the conduit 27 for flow through the passageway 28 and, hence, on to the inlet of the compressor 15.
  • all or part of the effluent may be passed through control valve 44 and conduit 45 for flow through passageway 46 of the heat exchange device 32 to provide refrigeration for the cycle as described below.
  • the second part of the cooled high pressure refrigerant gas is further cooled upon flowing through the passageway 31 of the heat exchange device 32 and then expanded in valve 47 to a pressure slightly above the suction pressure of the compressor to effect its partial liquefaction, and then fed by conduit 48 to phase separator 49 where the liquefied refrigerant collects in a pool 50.
  • the liquefied refrigerant may be employed to cool an external fluid flowed by conduit 51 having a control valve 52 through coil 53 immersed in the pool 50. Also, when the cycle is employed as a liquefier, liquefied refrigerant may be withdrawn from the phase separator through conduit 54 having a control valve 55.
  • Gaseous refrigerant comprising un- Iiquefied refrigerant gas fed to the phase separator and liquid refrigerant that may be vaporized in the phase separator is withdrawn from the phase separator through conduit 56 and merged with the refrigerant gas in the conduit 45 for flow through the passageways 46 and 28.
  • Makeup refrigerant gas for the cycle is fed to the suction inlet of the compressor 15 by conduit 57 and, when the makeup refrigerant gas is available at a pressure lower than suction pressure of the compressor 15, the makeup refrigerant gas is fed by conduit 58 through a suitable compressor 59 to the conduit 57.
  • the power developed by the work expansion of the high temperature high pressure refrigerant gas in the turbine expander 12 and the power developed by the work expansion of the low temperature high pressure refrigerant gas in the turbine expander 13 is applied directly through the common shaft 14 to the compressor 11 to provide the sole power source for the final compressor stage.
  • the expander-compressor-expander unit 10 is characterized so that the expansion turbines 12 and 13, although rotating at the same speed and notwithstanding the material difference between their operating temperatures, both operate at a high order of efficiency to satisfy fully the work expansion refrigeration producing requirements of the cycle and both develop a high percentage of the potential power of the work expansion which is utilized to drive the final stage of compression which makes possible, although the final compression stage is rotating at the same speed as the expansion turbines, compression of the refrigerant gas to the required high pressure from a lower intermediate pressure thereby reducing the requirements of the first stage of compression and achieving a reduction in capital expenditure and operating power.
  • the flow of high pressure refrigerant gas discharged from the compressor 11 is sufficient to satisfy the required flow of refrigerant gas to the expansion turbines and also provides high pressure refrigerant gas that is partially liquefied upon expansion in valve 47.
  • the expander-compressor-expander unit 10 includes a casing 60, which may be made up of sections bolted or otherwise removably secured together, forming a housing for the compressor 11, the turbine expander 12 and the turbine expander 13.
  • a shaft 61 is rotatably supported within the casing 60 by journal thrust bearings 62 and 63, preferably of the tilting pad type, spaced axially of the shaft 61 and located inwardly of shaft ends 64 and 65.
  • An impeller 66 of the compressor 11 is mounted on the shaft 61 for rotation therewith at a point intermediate the bearings 62 and 63 and the impeller 66 includes radial blades 67 which are of constant radius at its input.
  • Internal walls 68 of the casing provide a chamber 69 within which the impeller 66 rotates and an inlet passageway 70 and an outlet passageway 71 communicating with the chamber 69.
  • the inlet passageway 70 extends circumferentially about the shaft 61 and includes a portion 72 which extends from the outer regions of the casing 60, where it communicates with fluid inlet 73, radially toward the shaft 61 and a portion 74 which extends axially of the shaft and merges with the chamber 69 at the inlet of the impeller 66.
  • the outlet passageway 71 extends circumferentially about the shaft 61 radially outwardly from communication with the chamber 69 at the discharge of the impeller 66.
  • passageway 71 functions as a diffuser which may be of the vaneless type and discharges into a volute 75 which communicates with discharge outlet 76.
  • the turbine expander 12 includes an impeller 77 mounted on and secured to the shaft end 65 and the turbine expander 13 includes an impeller 78 mounted on and secured to the shaft end 64.
  • the turbine expanders 12 and 13 are of the radial inflow or centripetal type and the impellers 77 and 78 are provided with radial blades 79, preferably of the open type, having an axial dimension at the periphery of the impellers corresponding substantially to the width of the nozzle inlet and a substantially greater dimension, measured in a plane perpendicular to the axis of rotation, at the exit of the impeller.
  • internal walls 80 of the casing 60 define a chamber 81 within which the impeller 77 rotates, the chamber 81 being shaped to conform to the outer configuration of the blades 79.
  • the internal walls 80 also define a fluid inlet passageway 82 and an exhaust passageway 83 which diverges in the direction of flow and is of circular cross section concentric with the axis of rotation of the impeller.
  • the inlet passageway 82 extends circumferentially about the impeller 77 and communicates with the chamber 81 at the inlet 84 of the blades 79, and extends radially outwardly from the shaft into communication with a circumferentially extending chamber 85, also defined by internal walls 80 of the casing, into which high pressure gas to be expanded is fed by input conduit 86.
  • a plurality of spaced vanes are positioned in the passageway 82, in equally spaced relationship about the circumference of the impeller, to provide therebetween nozzles for directing the high pressure gas into the peripheral entries of the blades 79.
  • the vanes 90 are spaced radially from the peripheral edge 84 of the blades 79 to permit the high pressure gas discharged from the nozzles to follow a path influenced by the position of the vanes 90 and the vanes 90 are adjustable in unison to vary the mass and the direction of flow of the gas into the impeller.
  • each of the vanes 90 is mounted for pivotal movement about an axis parallel to the axis of rotation of the impeller by a shaft 93 supported in a wall 94 of the casing.
  • the shaft 93 On the side of the wall 94 opposite the passageway 82, the shaft 93 is connected to an arm 95 provided with a slot 96 which receives a pin 97 carried by a ring 98 positioned in concentric relation about the axis of rotation of the impeller and rotatably supported in a circular groove 99 of rectangular cross section formed in the wall 94.
  • a mechanism is provided for rotating the ring 98 relative to the wall 94 to simultaneously rotate each of the vanes 90 in the same direction and in the same degree about their respective supporting shafts 93.
  • Such mechanism includes a crank arm 100 connected outside of the casing 60 to an end of shaft 101 journaled in the casing, the other end of the shaft 101 being rigidly connected within the casing to one end of a crank arm 102.
  • the other end of the crank arm 102 is rigidly connected to shaft 103 secured to a rectangular block 104 received in a rectangular opening 105 formed in the ring 98.
  • the turbine expander 13 is constructed in a manner similar to the turbine expander 12 but is differently dimensioned as described below.
  • the impeller 78 is a mirror image of the impeller 77 and rotates within a chamber defined by internal walls 111 of the casing.
  • the internal walls 111 also define a divergent discharge passageway 112 and an inlet passageway 113, the latter passageway communicating with an inlet chamber 114 to which high pressure gas is supplied through input conduit 115.
  • Adjustable vanes 116 are located in the passageway 113 in a manner similar to the vanes 90 and a mechanism similar to the arrangement shown in FIG. 4 is provided to effect adjustment of the vanes upon movement of crank arm 100' connected to shaft 101.
  • Seals 120, 121, 122, and 123, of the labyrinth type, are pro vided about the shaft 61.
  • Seals 120 and 121 are located in wardly of the bearings 62, 63 on opposite sides of the compressor impeller 66, and function to impede the flow of high pressure gas along the shaft in a direction toward the turbine expanders, while seals 122 and 123, located between the hearing 62 and the impeller 78 and between the bearing 63 and the impeller 77, respectively, function to impede the flow of cold gas along the shaft inwardly toward the compressor impeller.
  • high pressure gas is fed to the seals 122 and 123 by passageways 124 and 125 leading from the seals 120 and 121 to the seals 122 and 123, respectively.
  • the incoming compressed gas is accelerated and directed by the nozzles and enters the peripheral inlet of the radial blades with a large tangential velocity and a small radial velocity and, upon flowing through the impeller, the kinetic energy of the gas is transferred to the impeller to efiect its rotation and the gas leaves the blades and enters the discharge passageway at a relatively low velocity.
  • the tangential velocity of the incoming gas and the linear velocity of the tips 84 of the radial blades should correspond within narrow limits.
  • the maximum permissible tip speed of the blades is one of the controlling parameters for expansion turbines operating at cryogenic temperatures.
  • the maximum linear velocity of the peripheral tips of the blades is usually selected to be equal to 0.8 of Mach. 1.
  • the optimum speed of the tips of the blades for given flow of a specific gas at a given pressure and temperature may be established by correlating the speed of rotation of the impeller and the diameter of the blades at the inlet of the impeller.
  • adjustable vanes such as the adjustable vanes 90 and 116 of the turbine expanders 12 and 13 makes it possible to vary the mass and the direction of the high velocity gas discharged from the nozzles which, together with the provision of a radial space between the periphery of the blades and the discharge end of the nozzles, makes it possible to operate the expansion turbines at the designed efficiency over a wide range of different input flow rates for a specific gas at a given pressure and temperature.
  • two expansion turbines and a compressor may be designed as a unitary structure with all of the impellers mounted on a common shaft and rotating at a common speed, with the expansion turbines and the compressor operating at high efficiency and with substantially the total potential horsepower of the expansion being developed by the expansion turbines and utilized as the sole power source for the compressor which delivers the pressurized gas to both expansion turbines and excess pressurized gas for liquefaction.
  • the foregoing has been accomplished, at least in part, by operating the expansion turbines at a constant input pressure or at a substantially equal pressure ratio, by operating the expansion turbines at substantially different temperature levels, by maintaining substantially equal flow to each of the expansion turbines, and by utilizing a constant input compressor.
  • the feature of rotating the compressor and both expansion turbines at the same speed permits the impeller of the compressor and the impellers of the expansion turbines to be mounted on a common shaft to provide a compact assembly which oifers special advantages in low temperature equipment especially in view of the high rotating speeds involved.
  • the further feature provided by the present invention of mounting the impellers of the two expansion turbines on opposite sides of the compressor impeller aids in balancing the machine and permits counter application of the thrust developed by the expansion turbine impellers and partial compensation of the thrust developed by the compressor impeller.
  • An expander-compressor-expander unit constructed in accordance with the principles of the present invention has been operated for extended periods of time in a refrigeration cycle of the type shown in FIG. 1.
  • the compressor was of the centrifugal type and included an open impeller with the radial blades at the periphery having a diameter of about 5.00 inches, the inlet nozzle and the diffuser being provided without vanes.
  • the turbine expanders were of the centripetal type having impellers provided with open radial blades; the impeller of the high temperature turbine expander having a diameter at its inlet of 5.25 inches and the impeller of the low temperature turbine expander having a diameter of 4.50 inches at its inlet.
  • the turbine expanders were provided with adjustable nozzles, as described above, and the nozzle control arms were ganged together for simultaneous control; however, means were provided for independent adjustment of the nozzles of each turbine expander.
  • the following table provides data on the performance of the expander-compressor-expander unit utilizing nitrogen as the refrigerant, the data being collected at different times during a period of continuous operation which exceeded 5 days:
  • Inlet pressure p.s.i.g 400 405 405 400 Inlet temperature
  • Inlet pressure p.s.i.g 525 535 535 530
  • Inlet temperature F... 17 21 22
  • Discharge pressure p.s.i.g 69 70
  • Discharge temperature F -120 123 -122 124
  • Flow standard cubic ieetfhourx 1,000 566 520 520 520 Adiabatic efliciency, percent 66. 5 67. 5 68. 6 69.
  • Horsepower 499 472 480 488 Low temperature expansion tur Inlet pressure p.s.i.g..
  • the cycle of FIG. 1 functioned as a closed system to provide sources of refrigeration for a low pressure air separation system to increase liquid producing capacity.
  • Compressed air to be separated flowed through the passageway 41 of the heat exchange device 40 and the liquid-vapor nitrogen mixture in conduit 48 was in- I troduced into the high pressure fractionating column and an equivalent mass of nitrogen vapor was withdrawn from the fractionating column by conduit 56.
  • the nitrogen gas was discharged from the compressor 11 at about 155 F. and under a pressure of about 545 p.s.i.g. and was divided with about 30 percent flowing through passageway 20 of heat exchange device 21 and with about 70 percent flowing through passageway 22 of heat exchange device 23.
  • the compressed nitrogen gas was cooled in heat exchange device 21 to about 17 F. in heat interchange with a freon refrigerant and was introduced into the inlet of the turbine expander 12 under a pressure of about 525 p.s.i.g.
  • the major portion of the nitrogen gas was cooled in heat exchange device 23 to about 1 78 F. and then divided with about percent being fed to the inlet of the turbine expander 13 under a pressure of about 520 p.s.i.g.
  • the remaining 20 percent of the high pressure nitrogen gas was cooled to about 276 F. upon flowing through the passageway 31 of the heat. exchange device 32, then expanded in valve 47 to about 75 p.s.i.g.
  • the cold nitrogen gas in the conduit 45 was merged with the nitrogen vapor at a temperature of 285 F. withdrawn from the phase separator 49, and the merged stream was warmed upon flowing through the passageway 46 of the heat exchange device 32 to about l79 F. and then combined with the nitrogen gas withdrawn from the passageway 38 at about 1 64 F.; the combined streams being warmed to about 75 F. upon flowing through the passageway 28 of the heat exchange device 23 and then returned to the inlet of the compressor by way of the conduit 17.
  • the nitrogen gas flowing through the passageway 39 of the heat exchange device 40 was withdrawn from that passageway at about 84 F. and conducted by conduit 42 to the conduit 17 onto the inlet of the compressor 15.
  • Process for producing refrigeration as defined in claim 1 including the further step of utilizing thrust developed by one of the expansion turbines to counterbalance thrust developed by the centrifugal compressor.
  • Process for producing refrigeration as defined in claim 1 including the further step of cooling a third portion of the relatively high pressure gas to a third relatively low temperature below the second temperature

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  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Separation By Low-Temperature Treatments (AREA)
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US3874185A (en) * 1972-12-18 1975-04-01 Linde Ag Process for a more efficient liquefaction of a low-boiling gaseous mixture by closely matching the refrigerant warming curve to the gaseous mixture cooling curve
EP0248578A2 (en) * 1986-06-02 1987-12-09 Normalair-Garrett (Holdings) Limited Air cycle cooling systems
US4894076A (en) * 1989-01-17 1990-01-16 Air Products And Chemicals, Inc. Recycle liquefier process
US4970867A (en) * 1989-08-21 1990-11-20 Air Products And Chemicals, Inc. Liquefaction of natural gas using process-loaded expanders
US6085545A (en) * 1998-09-18 2000-07-11 Johnston; Richard P. Liquid natural gas system with an integrated engine, compressor and expander assembly
US6085546A (en) * 1998-09-18 2000-07-11 Johnston; Richard P. Method and apparatus for the partial conversion of natural gas to liquid natural gas
US6085547A (en) * 1998-09-18 2000-07-11 Johnston; Richard P. Simple method and apparatus for the partial conversion of natural gas to liquid natural gas
US6269656B1 (en) 1998-09-18 2001-08-07 Richard P. Johnston Method and apparatus for producing liquified natural gas
US6526775B1 (en) * 2001-09-14 2003-03-04 The Boeing Company Electric air conditioning system for an aircraft
US20050126204A1 (en) * 2003-12-12 2005-06-16 Visteon Global Technologies, Inc. Air-cycle air conditioning system for commercial refrigeration
US20080240907A1 (en) * 2007-03-29 2008-10-02 Seiichiro Yoshinaga Expansion turbine having a variable nozzle mechanism
US20080240908A1 (en) * 2007-03-29 2008-10-02 Toshio Takahashi Expansion turbine having a variable nozzle mechanism
EP2508748A1 (en) * 2011-04-04 2012-10-10 Ebara International Corporation Cryogenic pressurized liquefied gas expander
US9739200B2 (en) * 2013-12-30 2017-08-22 Rolls-Royce Corporation Cooling systems for high mach applications
US20180066888A1 (en) * 2016-08-29 2018-03-08 Stanislav Sinatov Method for Electrical Energy Storage with Co-production of Liquefied Methaneous Gas
US20180073802A1 (en) * 2016-09-12 2018-03-15 Stanislav Sinatov Method for Energy Storage with Co-production of Peaking Power and Liquefied Natural Gas
US10731795B2 (en) * 2017-08-28 2020-08-04 Stanislav Sinatov Method for liquid air and gas energy storage
WO2023287295A1 (en) * 2021-07-16 2023-01-19 Skomsvold Aage A device to produce higher pressure and temperature in a gas

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JPS58188000U (ja) * 1982-06-08 1983-12-14 株式会社日本製鋼所 荷電粒子加速器のイオン源コ−ン
US4904158A (en) * 1988-08-18 1990-02-27 Union Carbide Corporation Method and apparatus for cryogenic liquid expansion
US5186013A (en) * 1989-02-10 1993-02-16 Thomas Durso Refrigerant power unit and method for refrigeration
CN113503691B (zh) * 2021-07-12 2022-11-22 北京中科富海低温科技有限公司 一种两级压缩循环氮气液化装置及其液化方法

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US3194026A (en) * 1963-10-24 1965-07-13 Fleur Corp Power-refrigeration system
US3241327A (en) * 1963-12-18 1966-03-22 Fleur Corp Waste heat recovery in air fractionation
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Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3874185A (en) * 1972-12-18 1975-04-01 Linde Ag Process for a more efficient liquefaction of a low-boiling gaseous mixture by closely matching the refrigerant warming curve to the gaseous mixture cooling curve
EP0248578A2 (en) * 1986-06-02 1987-12-09 Normalair-Garrett (Holdings) Limited Air cycle cooling systems
EP0248578A3 (en) * 1986-06-02 1990-01-24 Normalair-Garrett (Holdings) Limited Air cycle cooling systems
US4894076A (en) * 1989-01-17 1990-01-16 Air Products And Chemicals, Inc. Recycle liquefier process
US4970867A (en) * 1989-08-21 1990-11-20 Air Products And Chemicals, Inc. Liquefaction of natural gas using process-loaded expanders
US6085545A (en) * 1998-09-18 2000-07-11 Johnston; Richard P. Liquid natural gas system with an integrated engine, compressor and expander assembly
US6085546A (en) * 1998-09-18 2000-07-11 Johnston; Richard P. Method and apparatus for the partial conversion of natural gas to liquid natural gas
US6085547A (en) * 1998-09-18 2000-07-11 Johnston; Richard P. Simple method and apparatus for the partial conversion of natural gas to liquid natural gas
US6269656B1 (en) 1998-09-18 2001-08-07 Richard P. Johnston Method and apparatus for producing liquified natural gas
US6526775B1 (en) * 2001-09-14 2003-03-04 The Boeing Company Electric air conditioning system for an aircraft
US20050126204A1 (en) * 2003-12-12 2005-06-16 Visteon Global Technologies, Inc. Air-cycle air conditioning system for commercial refrigeration
US6966198B2 (en) 2003-12-12 2005-11-22 Visteon Global Technologies, Inc. Air-cycle air conditioning system for commercial refrigeration
US20080240907A1 (en) * 2007-03-29 2008-10-02 Seiichiro Yoshinaga Expansion turbine having a variable nozzle mechanism
US20080240908A1 (en) * 2007-03-29 2008-10-02 Toshio Takahashi Expansion turbine having a variable nozzle mechanism
EP1988257A3 (en) * 2007-03-29 2009-02-18 IHI Corporation Expansion turbine with a variable guiding nozzle mechanism
US8113769B2 (en) 2007-03-29 2012-02-14 Ihi Corporation Expansion turbine having a variable nozzle mechanism
US8231339B2 (en) 2007-03-29 2012-07-31 Ihi Corporation Expansion turbine having a variable nozzle mechanism
EP2508748A1 (en) * 2011-04-04 2012-10-10 Ebara International Corporation Cryogenic pressurized liquefied gas expander
US8653687B2 (en) 2011-04-04 2014-02-18 Ebara International Corporation Liquefied gas expander nozzle ring having adjustable guide vanes
US9739200B2 (en) * 2013-12-30 2017-08-22 Rolls-Royce Corporation Cooling systems for high mach applications
US20180066888A1 (en) * 2016-08-29 2018-03-08 Stanislav Sinatov Method for Electrical Energy Storage with Co-production of Liquefied Methaneous Gas
US20180073802A1 (en) * 2016-09-12 2018-03-15 Stanislav Sinatov Method for Energy Storage with Co-production of Peaking Power and Liquefied Natural Gas
US10655913B2 (en) * 2016-09-12 2020-05-19 Stanislav Sinatov Method for energy storage with co-production of peaking power and liquefied natural gas
US10731795B2 (en) * 2017-08-28 2020-08-04 Stanislav Sinatov Method for liquid air and gas energy storage
WO2023287295A1 (en) * 2021-07-16 2023-01-19 Skomsvold Aage A device to produce higher pressure and temperature in a gas

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GB1282643A (en) 1972-07-19
BR6911526D0 (pt) 1973-02-08
NL6912406A (ja) 1970-02-17
DE1941200A1 (de) 1970-02-19
FR2015703A1 (ja) 1970-04-30
BE737381A (ja) 1970-02-12
JPS4911657B1 (ja) 1974-03-19

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