US20100263405A1 - Cryogenic Refrigeration Method And Device - Google Patents

Cryogenic Refrigeration Method And Device Download PDF

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Publication number
US20100263405A1
US20100263405A1 US12/742,751 US74275108A US2010263405A1 US 20100263405 A1 US20100263405 A1 US 20100263405A1 US 74275108 A US74275108 A US 74275108A US 2010263405 A1 US2010263405 A1 US 2010263405A1
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Prior art keywords
fluid
expansion
working
compressor
compressors
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US12/742,751
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English (en)
Inventor
Fabien Durand
Alain Ravex
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LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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Application filed by LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude filed Critical LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Assigned to L'AIR LIQUIDE SOCIETE ANONYME POUR L'ETUDE ET L'EXPLOITATION DES PROCEDES GEORGES CLAUDE reassignment L'AIR LIQUIDE SOCIETE ANONYME POUR L'ETUDE ET L'EXPLOITATION DES PROCEDES GEORGES CLAUDE ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RAVEX, ALAIN, DURAND, FABIEN
Publication of US20100263405A1 publication Critical patent/US20100263405A1/en
Abandoned legal-status Critical Current

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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
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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
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    • F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
    • F25J1/0062—Light or noble gases, mixtures thereof
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    • F25J1/0072—Nitrogen
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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
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    • F25J1/008—Hydrocarbons
    • F25J1/0082—Methane
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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
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    • F25J1/0095—Oxides of carbon, e.g. CO2
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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
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    • F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
    • F25J1/0097—Others, e.g. F-, Cl-, HF-, HClF-, HCl-hydrocarbons etc. or mixtures thereof
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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
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    • 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
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
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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
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0275—Construction and layout of liquefaction equipments, e.g. valves, machines adapted for special use of the liquefaction unit, e.g. portable or transportable devices
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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.
    • 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.
    • F25J1/0281—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc. characterised by the type of prime driver, e.g. hot gas expander
    • F25J1/0284—Electrical motor as the prime mechanical driver
    • 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
    • F25J1/0287—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings including an electrical motor
    • 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
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    • 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
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    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1401—Ericsson or Ericcson cycles
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    • F25J2270/00—Refrigeration techniques used
    • F25J2270/14—External refrigeration with work-producing gas expansion loop
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    • F25J2270/00—Refrigeration techniques used
    • F25J2270/90—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration
    • F25J2270/912—Liquefaction cycle of a low-boiling (feed) gas in a cryocooler, i.e. in a closed-loop refrigerator

Definitions

  • the present invention relates to a cryogenic refrigeration device and method.
  • the invention relates more particularly to a cryogenic refrigeration device for transferring heat from a cold source to a hot source via a working fluid flowing in a closed working circuit, the working circuit comprising in series: a compression portion, a cooling portion, an expansion portion and a heating portion.
  • the cold source may for example be liquid nitrogen for cooling and the hot source water or air.
  • Refrigerators known for cooling superconductor elements generally use a reverse Brayton cycle. These known refrigerators use a lubricated rotary screw compressor, a countercurrent plate heat exchanger and an expansion turbine.
  • the invention proposes a cryogenic refrigeration device for transferring heat from a cold source to a hot source via a working fluid flowing through a closed working circuit, the working circuit comprising in series: a portion for the substantially isothermal compression of the fluid, a portion for the substantially isobaric cooling of the fluid, a portion for the substantially isothermal expansion of the fluid, and a portion for the substantially isobaric heating of the fluid, the compression portion of the working circuit comprising at least two compressors disposed in series and at least one heat exchanger for cooling the compressed fluid disposed at the outlet of each compressor, the expansion portion of the working circuit comprising at least one expansion turbine and at least one heat exchanger for heating the expanded fluid, the compressors and the expansion turbine(s) being driven by at least one high-speed motor comprising an output shaft whereof one end supports and rotates, by means of direct coupling, a first compressor and whereof the other end supports and rotates, by means of direct coupling, a second compressor or an expansion turbine.
  • the embodiments serve to obtain a system without oil pollution and without contact. This is because the combination of centrifugal compressors, centripetal turbines and bearings according to the invention reduces or eliminates any contact with the fixed parts and the rotating parts. This serves to avoid any risk of leakage.
  • the overall system is in fact hermetically sealed and does not comprise any rotary seal with regard to the atmosphere (such as mechanical seals or dry face seals).
  • embodiments of the invention may comprise one or more of the following features:
  • the invention further proposes a cryogenic refrigeration method for transferring heat from a cold source to a hot source via a working fluid flowing through a closed working circuit, the working circuit comprising in series: a compression portion comprising at least two compressors disposed in series, a fluid cooling portion, an expansion portion comprising at least one expansion turbine, and a heating portion, the method comprising a working cycle comprising a first step of substantially isothermal compression of the fluid in the compression portion by cooling the compressed fluid at the outlet of the compressors, a second step of substantially isobaric cooling of the fluid in the cooling portion, a third step of substantially isothermal expansion of the fluid in the expansion portion by heating the expanded fluid at the turbine outlet, and a fourth step of substantially isobaric heating of the fluid having exchanged heat with the cold source, the fluid working cycle (temperature T, entropy S) being of the reverse Ericsson type.
  • embodiments of the invention may comprise one or more of the following features:
  • FIG. 1 is a schematic view showing the structure and operation of a first exemplary embodiment of the refrigeration device according to the invention
  • FIG. 2 schematically shows a detail of FIG. 1 showing an arrangement of a drive motor of a compressor-compressor or compressor-turbine assembly
  • FIG. 3 schematically shows an example of a working cycle of the working fluid of the refrigerator in FIG. 1 ,
  • FIG. 4 is a schematic view showing the structure and operation of a second exemplary embodiment of a refrigerator according to the invention.
  • FIG. 5 schematically shows a second example of a working cycle of the working fluid of the refrigerator in FIG. 3 .
  • the refrigerator according to the invention is suitable for transferring heat from a cold source 15 at a cryogenic temperature to a hot source at ambient temperature 1 for example.
  • the cold source 15 may, for example, be liquid nitrogen for cooling and the hot source 1 may be water or air.
  • the refrigerator shown in FIG. 1 uses a working circuit 200 of a working gas comprising the components listed below.
  • the circuit 200 comprises a plurality of centrifugal compressors 3 , 5 , 7 disposed in series and operating at ambient temperature.
  • the circuit 200 comprises a plurality of heat exchangers 2 , 4 , 6 operating at ambient temperature disposed respectively at the outlet of the compressors 3 , 5 , 7 .
  • the temperatures of the working gas at the inlet and outlet of each compression stage are kept by the heat exchangers at a substantially identical level (cf. zone A in FIG. 3 which shows a gas working cycle: temperature in K as a function of the entropy S in J/kg).
  • zone A in FIG. 3 which shows a gas working cycle: temperature in K as a function of the entropy S in J/kg.
  • This arrangement serves to approach isothermal compression.
  • the inlet and outlet temperatures of each compression stage are substantially the same.
  • the heat exchangers 2 , 4 , 6 may be different or may be composed of distinct portions of the same heat exchanger in heat exchange with the hot source 1 .
  • the refrigerator comprises a plurality of high-speed motors ( 70 cf. FIG. 2 ).
  • high-speed motor normally means motors whereof the speed of rotation allows a direct coupling with a centrifugal compression stage or a centripetal expansion stage.
  • the high-speed motors 70 preferably use magnetic or dynamic gas bearings 171 ( FIG. 2 ).
  • a high-speed motor typically rotates at a speed of 10 000 rpm or several tens of thousands of rpm.
  • a low-speed motor rotates at a speed of a few thousand rpm.
  • the refrigerator Downstream of the compression portion comprising the compressors in series, the refrigerator comprises a heat exchanger 8 preferably of the countercurrent plate type separating the elements at ambient temperature (in the upper part of the circuit 200 shown in FIG. 1 ) from the elements at cryogenic temperature (in the lower part of the circuit 200 ).
  • the fluid is cooled (corresponding to zone D in FIG. 3 ).
  • the cooling of the gas from ambient temperature to cryogenic temperature takes place by countercurrent exchange with the same working gas at cryogenic temperature, which originates from the expansion portion after heat exchange with the cold source 15 .
  • the circuit Downstream of this cooling portion comprising the plate heat exchanger 8 , the circuit comprises one or more expansion turbines 9 , 11 , 13 , preferably of the centripetal type, disposed in series.
  • the turbines 9 , 11 , 13 operate at cryogenic temperature, the inlet and outlet temperatures of each expansion stage (turbine inlet and outlet) are kept substantially identical by one or more cryogenic heat exchangers 10 , 12 , 14 disposed at the outlet of the turbine(s).
  • the descending portions of zone C each corresponding to an expansion stage while the rising portions of this zone correspond to the heating in the heat exchangers 10 , 12 , 14 .
  • This arrangement serves to approach an isothermal expansion.
  • the inlet and outlet temperatures of each expansion stage are substantially the same.
  • the increase in the working gas temperature in the heat exchanger(s) ( 10 , 12 , 14 ) may be substantially identical (in absolute value) to the drop in the temperature of the fluid to be cooled ( 15 ) (cold source).
  • These heating heat exchangers 10 , 12 , 14 may be different or may be composed of distinct portions of the same heat exchanger exchanging heat with the cold source 15 .
  • the working fluid Downstream of the expansion and heat exchange portion with the cold source 15 , the working fluid again exchanges heat with the plate heat exchanger 8 (zone B in FIG. 3 ). The fluid exchanges heat in the heat exchanger 8 in countercurrent to its passage after the compression portion. After heating, the fluid returns to the compression portion and can repeat its cycle.
  • the circuit may further comprise a chamber of working gas at ambient temperature (not shown for the sake of simplification) to limit the pressure in the circuits, during the shutdown of the refrigerator for example.
  • the refrigerator preferably uses as working fluid a fluid in the gas phase flowing in a closed circuit.
  • a fluid in the gas phase flowing in a closed circuit This is composed for example of a pure gas or a mixture of pure gases.
  • gases for this technology are in particular: helium, neon, nitrogen, oxygen and argon. Carbon monoxide and methane may also be used.
  • the refrigerator is designed and thus operated so as to obtain a fluid working cycle approaching the reverse Ericsson cycle. This means: an isothermal compression, an isobaric cooling, an isothermal expansion and an isobaric heating.
  • the refrigerator in order to drive at least the compressors 3 , 5 , 7 (that is to drive the compressor impellers), the refrigerator uses a plurality of high-speed motors 70 .
  • each high-speed motor 70 accommodates a compressor impeller 31 on one end of its output shaft and, on the other end of its output shaft, another compressor impeller or a turbine wheel 9 .
  • This arrangement provides many advantages.
  • This configuration allows a direct coupling in the refrigerator between the motor 70 and the impellers of the compressor 3 , 5 , 7 or between the motor 70 and the wheels of the turbines 9 , 11 , 13 .
  • This serves to do without a speed step-up gear or reducer (thereby limiting the number of moving parts required).
  • This configuration also allows the utilization of the mechanical work of the turbine(s) 9 , 11 , 13 and in consequence, an increase in the total energy efficiency of the refrigerator.
  • the refrigerator operates without oil, thereby guaranteeing the purity of the working gas and eliminating the need for a de-oiling operation.
  • the number of high-speed motors mainly depends on the energy efficiency desired for the refrigerator. The higher this efficiency, the higher the number of high-speed motors.
  • the ratio between the number of compression stages (compressors) and the number of expansion stages (turbines) depends on the target cold temperature. For example, for a refrigerator of which the cold source is at 273 K, the number of compression stages is substantially equal to the number of expansion stages. For a refrigerator in which the cold source is at 65 K, the number of compression stages is about 3 times higher than the number of expansion stages.
  • FIG. 4 shows another embodiment which can be used for example to cool or maintain the temperature of superconductor cables at a cryogenic temperature of about 65 K.
  • the number of compression stages compressors
  • the number of expansion stages turbines. This can be obtained in several possible configurations. For example, three compressors and one turbine or six compressors and two turbines.
  • the refrigerator comprises six compressors 101 , 102 , 103 , 104 , 105 , 106 and two turbines 116 , 111 and four high-speed motors 107 , 112 , 114 , 109 .
  • the first two compressors 101 , 102 (that is the compressor impellers) are mounted respectively at the two ends of a first high-speed motor 107 .
  • the next two compressors 103 , 104 are mounted respectively on the two ends of a second high-speed motor 112 .
  • the next compressor 105 and the turbine 116 (that is the turbine wheel) are mounted respectively on the two ends of a third high-speed motor 114 .
  • the last turbine 111 and the sixth compressor 106 are mounted respectively on the two ends of a fourth motor 109 .
  • the gas is progressively compressed by passing in succession through the four compressors in series 101 , 102 , 103 , 104 , 105 , 106 .
  • each compression stage On completion of each compression stage (at the outlet of each compressor) the working gas is cooled in a respective heat exchanger 108 (by heat exchange with air or water for example) to approach isothermal compression. After this compression portion, the gas is isobarically cooled through a countercurrent plate heat exchanger 103 . After this cooling portion, the cooling gas is progressively expanded in the two centripetal turbines in series 116 , 111 . After each expansion stage the working gas is heated by heat exchange in a heat exchanger 110 (for example by heat exchange with the cold source), in order to obtain a substantially isothermal expansion. On completion of this isothermal expansion, the working gas is heated in the heat exchanges 113 and can then start a new cycle by a compression.
  • a heat exchanger 110 for example by heat exchange with the cold source
  • FIG. 5 shows the cycle (temperature T and entropy S) of the working fluid of the refrigerator in FIG. 5 .
  • six sawteeth can be distinguished in the compression zone A, corresponding to the six successive compressions and coolings.
  • the expansion zone C two sawteeth are identified, corresponding to the two successive expansions and heatings.
  • the invention improves the cryogenic refrigerators in terms of energy efficiency, reliability and size.
  • the invention serves to decrease the number of maintenance operations and to eliminate the use of oils.
  • one or both ends of the output shafts of the motor(s) can directly drive more than one wheel (that is a plurality of compressors or a plurality of turbines).

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  • Engineering & Computer Science (AREA)
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  • Thermal Sciences (AREA)
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  • Health & Medical Sciences (AREA)
  • Emergency Medicine (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
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  • Structures Of Non-Positive Displacement Pumps (AREA)
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US12/742,751 2007-11-23 2008-10-23 Cryogenic Refrigeration Method And Device Abandoned US20100263405A1 (en)

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FR0759243A FR2924205B1 (fr) 2007-11-23 2007-11-23 Dispositif et procede de refrigeration cryogenique
FR0759243 2007-11-23
PCT/FR2008/051919 WO2009066044A2 (fr) 2007-11-23 2008-10-23 Dispositif et procede de refrigeration cryogenique

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JP (1) JP2011504574A (fr)
KR (1) KR20100099129A (fr)
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DK (1) DK2225501T3 (fr)
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US20120266630A1 (en) * 2009-10-27 2012-10-25 Jean-Paul Laugier Method for fractionating a stream of cracked gas to obtain an ethylene-rich cut and a stream of fuel, and related installation
US10767924B2 (en) * 2009-10-27 2020-09-08 Technip France Method for fractionating a stream of cracked gas to obtain an ethylene-rich cut and a stream of fuel, and related installation
US9557101B2 (en) 2011-06-24 2017-01-31 Saipem S.A. Method for liquefying natural gas with a triple closed circuit of coolant gas
WO2012175887A3 (fr) * 2011-06-24 2013-11-14 Saipem S.A. Procede de liquefaction de gaz naturel avec un melange de gaz refrigerant
AU2012273829B2 (en) * 2011-06-24 2016-05-26 Saipem S.A. Method for liquefying natural gas with a triple closed circuit of coolant gas
WO2012175889A3 (fr) * 2011-06-24 2013-11-14 Saipem S.A. Procédé de liquéfaction de gaz naturel a triple circuit ferme de gaz réfrigérant
AU2012273829C1 (en) * 2011-06-24 2017-03-16 Saipem S.A. Method for liquefying natural gas with a triple closed circuit of coolant gas
US9777959B2 (en) 2011-06-24 2017-10-03 Saipem S.A. Method for liquefying natural gas with a mixture of coolant gas
WO2014005229A1 (fr) * 2012-07-04 2014-01-09 Kairama Inc. Gestion de température pour compression et expansion de gaz
US9234480B2 (en) 2012-07-04 2016-01-12 Kairama Inc. Isothermal machines, systems and methods
US20140186170A1 (en) * 2012-12-27 2014-07-03 Ronald E. Graf Centrifugal Expanders And Compressors Each Using Rotors In Both Flow Going From Periphery To Center And Flow Going From Center To Periphery Their Use In Engines Both External Heat And Internal Combustion. Means to convert radial inward flow to radial outward flow with less eddy currents
US10072665B1 (en) 2012-12-27 2018-09-11 Ronald E. Graf Multistage compressors and reverse compressors comprising a series of centrifugal pumps alternating flow toward and away from axle with better flow transitions between stages
US10393428B2 (en) * 2013-12-06 2019-08-27 L'air Liquide Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Device and method for cooling and/or low-temperature liquefaction
US20200080771A1 (en) * 2017-03-14 2020-03-12 Woodside Energy Technologies Pty Ltd Containerised lng liquefaction unit and associated method of producing lng
US12111100B2 (en) * 2017-03-14 2024-10-08 Woodside Energy Technologies Pty Ltd Containerised LNG liquefaction unit and associated method of producing LNG
US20220333830A1 (en) * 2017-10-09 2022-10-20 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Refrigeration device and method
US11408648B2 (en) * 2017-10-09 2022-08-09 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Refrigeration device and method
KR20190040123A (ko) * 2017-10-09 2019-04-17 레르 리키드 쏘시에떼 아노님 뿌르 레？드 에렉스뿔라따시옹 데 프로세데 조르즈 클로드 냉각을 위한 장치 및 프로세스
KR102508257B1 (ko) * 2017-10-09 2023-03-08 레르 리키드 쏘시에떼 아노님 뿌르 레드 에렉스뿔라따시옹 데 프로세데 조르즈 클로드 냉각을 위한 장치 및 프로세스
AU2018348842B2 (en) * 2017-10-09 2023-12-14 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Refrigeration device and method
CN112212534A (zh) * 2019-07-10 2021-01-12 乔治洛德方法研究和开发液化空气有限公司 制冷和/或液化设备
CN114270116A (zh) * 2019-08-05 2022-04-01 乔治洛德方法研究和开发液化空气有限公司 制冷装置和系统
US20220268516A1 (en) * 2019-08-05 2022-08-25 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Cooling and/or liquefying system and method
US20230296294A1 (en) * 2020-08-12 2023-09-21 Cryostar Sas Simplified cryogenic refrigeration system
FR3119667A1 (fr) * 2021-02-10 2022-08-12 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Dispositif et procédé de liquéfaction d’un fluide tel que l’hydrogène et/ou de l’hélium
WO2022171392A1 (fr) * 2021-02-10 2022-08-18 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Dispositif et procédé de liquéfaction d'un fluide tel que l'hydrogène et/ou de l'hélium
WO2022171390A1 (fr) * 2021-02-10 2022-08-18 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Dispositif et procédé de liquéfaction d'un fluide tel que l'hydrogène et/ou de l'hélium
WO2022171391A1 (fr) * 2021-02-10 2022-08-18 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Dispositif et procédé de liquéfaction d'un fluide tel que l'hydrogène et/ou de l'hélium

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CN101868677B (zh) 2012-10-03
ES2693066T3 (es) 2018-12-07
FR2924205B1 (fr) 2013-08-16
CN101868677A (zh) 2010-10-20
EP3410035A1 (fr) 2018-12-05
EP2225501B1 (fr) 2018-09-05
EP2225501A2 (fr) 2010-09-08
WO2009066044A3 (fr) 2009-07-16
DK2225501T3 (en) 2018-11-19
WO2009066044A2 (fr) 2009-05-28
HUE040042T2 (hu) 2019-02-28
FR2924205A1 (fr) 2009-05-29
WO2009066044A4 (fr) 2009-09-11
PL2225501T3 (pl) 2019-02-28
JP2011504574A (ja) 2011-02-10
EP3561411A1 (fr) 2019-10-30
KR20100099129A (ko) 2010-09-10

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