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EP2225501B1 - Cryogenic refrigeration method and device - Google Patents

Cryogenic refrigeration method and device Download PDF

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Publication number
EP2225501B1
EP2225501B1 EP08852903.7A EP08852903A EP2225501B1 EP 2225501 B1 EP2225501 B1 EP 2225501B1 EP 08852903 A EP08852903 A EP 08852903A EP 2225501 B1 EP2225501 B1 EP 2225501B1
Authority
EP
European Patent Office
Prior art keywords
fluid
expansion
working
compressors
turbine
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.)
Active
Application number
EP08852903.7A
Other languages
German (de)
French (fr)
Other versions
EP2225501A2 (en
EP2225501B2 (en
Inventor
Fabien Durand
Alain Ravex
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.)
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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Application filed by Air Liquide SA, LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude filed Critical Air Liquide SA
Priority to PL08852903.7T priority Critical patent/PL2225501T5/en
Priority to EP19174805.2A priority patent/EP3561411A1/en
Priority to EP18178529.6A priority patent/EP3410035A1/en
Publication of EP2225501A2 publication Critical patent/EP2225501A2/en
Application granted granted Critical
Publication of EP2225501B1 publication Critical patent/EP2225501B1/en
Publication of EP2225501B2 publication Critical patent/EP2225501B2/en
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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
    • 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
    • F25J1/0062—Light or noble gases, mixtures thereof
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    • 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
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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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    • F25J1/0075—Oxygen
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    • F25J1/007—Primary atmospheric gases, mixtures thereof
    • F25J1/0077—Argon
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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
    • F25J1/008—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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    • F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
    • 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
    • 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
    • F25J1/0097—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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    • F25J1/00—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
    • F25J1/0257—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
    • F25J1/0276—Laboratory or other miniature devices
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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.
    • 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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    • F25J1/0243—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
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    • 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 more particularly relates to a cryogenic refrigeration device for transferring heat from a cold source to a hot source via a working fluid circulating in a closed work circuit, the working circuit comprising in series: a portion of compression, a cooling portion, a detent portion and a warming portion.
  • the cold source may be, for example, liquid nitrogen to be cooled and the hot source of water or air.
  • Refrigerators known to cool superconducting elements generally use a reverse Brayton cycle. These known refrigerators use a screw-lubricated compressor, a countercurrent plate heat exchanger and an expansion turbine.
  • the document US 3494145 describes a refrigeration system using geared couplings requiring oil bearings.
  • This type of device uses rotating joints such as mechanical seals between the working gas and the gear housing and oil bearings.
  • This architecture increases the risk of leakage of the working gas and the possible pollution of the working gas by the oil.
  • This system also relates to a low speed type motor.
  • An object of the present invention is to overcome all or part of the disadvantages of the prior art noted above.
  • the invention proposes a cryogenic refrigeration device for transferring heat from a cold source to a hot source via a working fluid circulating in a closed working circuit, the working circuit comprising in series: a substantially isothermal compression portion of the fluid, a substantially isobaric cooling portion of the fluid, a substantially isothermal expansion portion of the fluid and a substantially isobaric heating portion of the fluid, the compression portion of the working circuit comprising at least two compressors arranged in series and at least one compressed fluid cooling exchanger disposed at the outlet of each compressor, the expansion portion of the working circuit comprising at least one expansion turbine and at least one expanded fluid heating exchanger, the compressors and the or the expansion turbines being driven by at least one engine said to high fast sse comprising an output shaft whose one end carries and rotates by direct coupling a first compressor and the other end carries and rotates by direct coupling an expansion turbine.
  • the embodiments make it possible to obtain a system without oil pollution and without contact. Indeed, 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 avoids any risk of leakage.
  • the entire system is indeed hermetic and has no rotating joints vis-à-vis the atmosphere (such as mechanical seals or "dry face seal").
  • the refrigerator according to the invention is provided for transferring heat from a cold source 15 at a cryogenic temperature to a hot source at room temperature 1 for example.
  • the cold source 15 may be, for example, liquid nitrogen to be cooled and the hot source 1 of water or air.
  • the refrigerator shown in the figure 1 uses a working circuit 200 of a working gas comprising the components listed below.
  • the circuit 200 comprises a plurality of compressors 3, 5, 7 centrifugals arranged in series and operating at ambient temperature.
  • the circuit 200 comprises a plurality of heat exchangers 2, 4, 6 operating at ambient temperature respectively disposed at the output of the compressors 3, 5, 7.
  • the working gas temperatures at the inlet and at the outlet of each compression stage (c ') that is to say at the inlet and the outlet of each compressor 3, 5, 7), are maintained by the heat exchange at a substantially identical level (see zone A on the figure 3 which represents a working cycle of the gas: temperature in K according to the entropy S in J / kg).
  • zone A on the figure 3 which represents a working cycle of the gas: temperature in K according to the entropy S in J / kg.
  • the exchangers 2, 4, 6 may be distinct or consist of distinct portions of the same exchanger in heat exchange with the hot source 1.
  • the refrigerator comprises several engines (70 cf. figure 2 ) said at high speed.
  • high speed motor is usually meant motors whose rotational speed allows direct coupling with a centrifugal compression stage or a centripetal expansion stage.
  • High speed motors 70 preferably use magnetic or dynamic gas bearings 171 ( figure 2 ).
  • a high speed motor typically rotates at a rotational speed of 10,000 rpm or several tens of thousands of revolutions per minute.
  • a low-speed motor runs rather with a speed of a few thousand revolutions per minute.
  • the refrigerator Downstream of the compression portion comprising the compressors in series, the refrigerator comprises a heat exchanger 8 preferably of plate type against the current separating the elements at room temperature (in the upper part of the circuit 200 shown in FIG. figure 1 ) cryogenic temperature elements (in the lower part of the circuit 200).
  • the fluid is cool (corresponding to zone D of the figure 3 ).
  • the cooling of the gas from room temperature to cryogenic temperature is carried out by countercurrent exchange with the same gas working gas at cryogenic temperature which returns from the expansion portion after heat exchange with the cold source 15.
  • the circuit Downstream of this cooling portion constituted by the exchanger 8 with plates, the circuit comprises one or more turbines 9, 11, 13 of expansion, preferably centripetal type, arranged in series.
  • the turbines 9, 11, 13 operate at cryogenic temperature
  • the inlet and outlet temperatures of each expansion stage are maintained substantially identical by one or more cryogenic heat exchangers 10, 12, 14 disposed at the exit of the turbine or turbines.
  • the downward portions of the zone C each corresponding to a relaxation stage while the rising portions of this zone correspond to the heating in the exchangers 10, 12, 14.
  • This arrangement makes it possible to approach an isothermal expansion.
  • the inlet and outlet temperatures of each flash stage are substantially the same.
  • the increase of the temperature of the working gas in the exchanger or exchangers (10, 12, 14) may be substantially identical (in absolute value) to the decrease in the temperature of the refrigerator.
  • fluid to be cooled (15) (cold source).
  • These heat exchangers 10, 12, 14 may be distinct or consist of separate portions of the same exchanger in heat exchange with the cold source 15.
  • the working fluid thermally exchanges again with the heat exchanger 8 plates (zone B of the figure 3 ).
  • the fluid thermally exchanges in the exchanger 8 against the current relative to its passage after the compression portion. After reheating the fluid returns to the compression portion and can start a cycle again.
  • the circuit may further comprise a working gas capacity at room temperature (not shown for the sake of simplification) to limit the pressure in the circuits, during the stopping of the refrigerator for example.
  • the refrigerator preferably uses as a working fluid a gas phase fluid circulating in a closed circuit.
  • a gas phase fluid circulating in a closed circuit.
  • This consists for example of a pure gas or a mixture of pure gas.
  • gases best suited to this technology include: helium, neon, nitrogen, oxygen and argon. Carbon monoxide and methane can also be used.
  • the refrigerator is designed and controlled so as to obtain a working cycle of the fluid approaching the reverse Ericsson cycle. That is: isothermal compression, isobaric cooling, isothermal expansion and isobaric heating.
  • the refrigerator uses for the drive at least compressors 3, 5, 7 (that is to say, for driving the wheels of the compressors) several motors 70 said to high speeds.
  • each high-speed motor 70 receives on one end of its output shaft a compressor wheel 31 and, on the other end of its shaft, another compressor wheel or a turbine wheel 9.
  • This arrangement provides numerous advantages .
  • This configuration allows in the refrigerator a direct coupling between the motor 70 and the compressor wheels 3, 5, 7 or between the motor 70 and the wheels of the turbines 9, 11, 13. This makes it possible to overcome a multiplier or speed reducer (which limits the number of moving parts required).
  • This configuration also allows a valuation of the mechanical work of the turbine or turbines 9, 11, 13 and therefore an increase in the overall energy efficiency of the refrigerator.
  • the refrigerator has an oil-free operation, which ensures the purity of the working gas and eliminates the need for a de-oiling operation.
  • the number of high speed engines is mainly a function of the desired energy efficiency for the refrigerator. The higher this efficiency, the higher the number of high speed motors.
  • the ratio between the number of compression stage (compressors) and the number of expansion stages (turbines) is a function of the target cold temperature. For example, for a refrigerator whose cold source is 273 K, the number of compression stage will be substantially equal to the number of stage of relaxation. For a refrigerator with a cold source of 65 K, the number of compression stages is approximately 3 times greater than the number of stages of expansion.
  • the figure 4 illustrates another embodiment which can for example be used to cool or maintain superconducting cables at a cryogenic temperature of about 65 K.
  • the number of compression stages compressors
  • the number of stages of relaxation turbines. This can be done according to several possible configurations. For example three compressors and a 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 i.e. the compressor wheels
  • the two following compressors 103, 104 are respectively mounted at the two ends of a second high-speed motor 112.
  • the following compressor 105 and the turbine 116 (that is to say the wheel of the turbine) are respectively mounted at both ends of a third high-speed motor 114.
  • the last turbine 111 and the sixth compressor 106 are mounted respectively at both ends of a fourth engine 109.
  • the gas is gradually compressed by passing successively in the four series compressors 101, 102, 103, 104, 105, 106.
  • 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 get closer an isothermal compression.
  • the gas is isobarically cooled through a countercurrent plate heat exchanger 103.
  • the cooling gas is progressively expanded in the two series centripetal turbines 116, 111.
  • the working gas is heated by heat exchange in an exchanger 110 (for example by heat exchange with the cold source), so as to achieve a substantially isothermal expansion.
  • the working gas is reheated in the exchanger 113 and can then start a new cycle again by compression.
  • the figure 5 represents the cycle (temperature T and entropy S) of the working fluid of the refrigerator of the figure 5 .
  • the figure 3 in the compression zone A there are six sawtooths corresponding to the six successive compressions and coolings.
  • zone C of relaxation we recognize two sawtooth corresponding to two successive relaxation and warming.
  • the invention improves cryogenic refrigerators in terms of energy efficiency, reliability and size.
  • the invention makes it possible to reduce the 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 road (ie several compressors or several turbines).

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Description

La présente invention concerne un dispositif et un procédé de réfrigération cryogénique.The present invention relates to a cryogenic refrigeration device and method.

L'invention concerne plus particulièrement un dispositif de réfrigération cryogénique destiné à transférer de la chaleur d'une source froide vers une source chaude via un fluide de travail circulant dans un circuit de travail fermé, le circuit de travail comprenant en série : une portion de compression, une portion de refroidissement, une portion de détente et une portion de réchauffement.The invention more particularly relates to a cryogenic refrigeration device for transferring heat from a cold source to a hot source via a working fluid circulating in a closed work circuit, the working circuit comprising in series: a portion of compression, a cooling portion, a detent portion and a warming portion.

La source froide peut être par exemple de l'azote liquide à refroidir et la source chaude de l'eau ou de l'air.The cold source may be, for example, liquid nitrogen to be cooled and the hot source of water or air.

Des réfrigérateurs connus pour refroidir des éléments supraconducteurs utilisent en général un cycle de Brayton inverse. Ces réfrigérateurs connus utilisent un compresseur lubrifié à vis, un échangeur à contre courant à plaques et une turbine de détente.Refrigerators known to cool superconducting elements generally use a reverse Brayton cycle. These known refrigerators use a screw-lubricated compressor, a countercurrent plate heat exchanger and an expansion turbine.

Ces réfrigérateurs connus présentent de nombreux inconvénients parmi :

  • un faible rendement énergétique du cycle et par conséquent du réfrigérateur,
  • l'utilisation d'huile pour refroidir et lubrifier le compresseur, ceci impose une opération de déshuilage du gaz de travail après compression,
  • l'utilisation de joints tournants entre le moteur électrique et le compresseur,
  • le faible rendement isotherme de compression du compresseur,
  • la périodicité des opérations de maintenance.
These known refrigerators have many disadvantages among:
  • a low energy efficiency of the cycle and consequently of the refrigerator,
  • the use of oil to cool and lubricate the compressor, this requires a de-oiling operation of the working gas after compression,
  • the use of rotating joints between the electric motor and the compressor,
  • the low compressor isothermal efficiency of the compressor,
  • the frequency of maintenance operations.

Le document US-3,494,145 décrit un système de réfrigération utilisant des accouplements via engrenages nécessitant des paliers à huile. Ce type de dispositif utilise des joints tournants tels que les garnitures mécaniques entre le gaz de travail et le carter des engrenages et des paliers à huile. Cette architecture augmente les risques de fuite du gaz de travail et la pollution possible du gaz de travail par l'huile. Ce système concerne par ailleurs un moteur de type basse vitesse.The document US 3494145 describes a refrigeration system using geared couplings requiring oil bearings. This type of device uses rotating joints such as mechanical seals between the working gas and the gear housing and oil bearings. This architecture increases the risk of leakage of the working gas and the possible pollution of the working gas by the oil. This system also relates to a low speed type motor.

Le document US-4,984,432 décrit un système de réfrigération utilisant des compresseurs ou des turbines de type à anneau liquide fonctionnant avec un moteur à basse vitesse utilisant des paliers classiques tels que les roulements à billes. Cette technologie relève des compresseurs et turbines volumétriques.The document US 4984432 discloses a refrigeration system using liquid ring type compressors or turbines operating with a low speed motor using conventional bearings such as ball bearings. This technology concerns volumetric compressors and turbines.

Un but de la présente invention est de pallier tout ou partie des inconvénients de l'art antérieur relevés ci-dessus.An object of the present invention is to overcome all or part of the disadvantages of the prior art noted above.

A cette fin, l'invention propose un dispositif de réfrigération cryogénique destiné à transférer de la chaleur d'une source froide vers une source chaude via un fluide de travail circulant dans un circuit de travail fermé, le circuit de travail comprenant en série : une portion de compression sensiblement isotherme du fluide, une portion de refroidissement sensiblement isobare du fluide, une portion de détente sensiblement isotherme du fluide et une portion de réchauffement sensiblement isobare du fluide, la portion de compression du circuit de travail comprenant au moins deux compresseurs disposés en série et au moins un échangeur de refroidissement du fluide comprimé disposé à la sortie de chaque compresseur, la portion de détente du circuit de travail comprenant au moins une turbine de détente et au moins un échangeur de réchauffement du fluide détendu, les compresseurs et la ou les turbines de détente étant entraînés par au moins un moteur dit à haute vitesse comprenant un arbre de sortie dont l'une des extrémité porte et entraîne en rotation par accouplement direct un premier compresseur et dont l'autre extrémité porte et entraîne en rotation par accouplement direct une turbine de détente.To this end, the invention proposes a cryogenic refrigeration device for transferring heat from a cold source to a hot source via a working fluid circulating in a closed working circuit, the working circuit comprising in series: a substantially isothermal compression portion of the fluid, a substantially isobaric cooling portion of the fluid, a substantially isothermal expansion portion of the fluid and a substantially isobaric heating portion of the fluid, the compression portion of the working circuit comprising at least two compressors arranged in series and at least one compressed fluid cooling exchanger disposed at the outlet of each compressor, the expansion portion of the working circuit comprising at least one expansion turbine and at least one expanded fluid heating exchanger, the compressors and the or the expansion turbines being driven by at least one engine said to high fast sse comprising an output shaft whose one end carries and rotates by direct coupling a first compressor and the other end carries and rotates by direct coupling an expansion turbine.

Les modes de réalisation permettent d'obtenir un système sans pollution d'huile et sans contact. En effet, la combinaison de compresseurs centrifuges, des turbines centripètes et des paliers selon l'invention réduit ou supprime tout contact avec les parties fixes et les parties tournantes. Ceci permet d'éviter tout risque de fuite. L'ensemble du système est en effet hermétique et ne comporte aucun joint tournant vis-à-vis de l'atmosphère (tel que des garnitures mécaniques ou des « dry face seal »).The embodiments make it possible to obtain a system without oil pollution and without contact. Indeed, 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 avoids any risk of leakage. The entire system is indeed hermetic and has no rotating joints vis-à-vis the atmosphere (such as mechanical seals or "dry face seal").

Par ailleurs, l'invention comporte en outre les caractéristiques suivantes :

  • les compresseurs sont du type à compression centrifuge,
  • la ou les turbines de détente sont du type à détente centripète,
  • les arbres de sortie des moteurs sont montés sur des paliers de type magnétique ou de type dynamique à gaz, lesdits paliers étant utilisés pour sustenter les compresseurs et les turbines,
  • la portion de refroidissement et la portion de réchauffement comprennent un échangeur de chaleur commun dans lequel le fluide de travail transite à contre-courant selon qu'il est refroidit ou réchauffé,
En outre, des modes de réalisation particuliers peuvent également comporter les caractéristiques suivantes :
  • le circuit de travail comprend un volume formant une capacité tampon de stockage du fluide de travail,
  • le fluide de travail est en phase gazeuse et constitué d'un gaz pur ou d'un mélange de gaz purs parmi : l'hélium, le néon, l'azote, l'oxygène, l'argon, le monoxyde de carbone, le méthane, ou tout autre fluide présentant une phase gazeuse à la température de la source froide.
Moreover, the invention furthermore comprises the following features:
  • the compressors are of the centrifugal compression type,
  • the expansion turbine or turbines are of the centripetal expansion type,
  • the output shafts of the motors are mounted on bearings of magnetic type or dynamic gas type, said bearings being used to support compressors and turbines,
  • the cooling portion and the heating portion comprise a common heat exchanger in which the working fluid transits countercurrently as it is cooled or heated,
In addition, particular embodiments may also include the following features:
  • the working circuit comprises a volume forming a buffer storage capacity of the working fluid,
  • the working fluid is in the gas phase and consists of a pure gas or a mixture of pure gases among: helium, neon, nitrogen, oxygen, argon, carbon monoxide, methane, or any other fluid having a gaseous phase at the temperature of the cold source.

L'invention propose en outre un procédé de réfrigération cryogénique destiné à transférer de la chaleur d'une source froide vers une source chaude via un fluide de travail circulant dans un circuit de travail fermé, le circuit de travail comprenant en série : une portion de compression comprenant au moins deux compresseurs disposés en série, une portion de refroidissement du fluide, une portion de détente comprenant au moins une turbine de détente, et une portion de réchauffement, le procédé comprenant un cycle de travail comportant une première étape de compression sensiblement isotherme du fluide dans la portion de compression par refroidissement du fluide comprimé en sortie des compresseurs, une seconde étape de refroidissement sensiblement isobare du fluide dans la portion de refroidissement, une troisième étape de détente sensiblement isotherme du fluide dans la portion de détente par réchauffement du fluide détendu en sortie de turbine, et une quatrième étape de réchauffement sensiblement isobare du fluide ayant échangé thermiquement avec la source froide, le cycle de travail du fluide (température T, entropie S) étant du type Ericsson inverser selon la revendication 6. Par ailleurs :

  • lors de la première étape de compression sensiblement isotherme, le fluide comprimé est refroidit en sortie de chaque compresseur pour maintenir les températures du fluide en entrée et en sortie de chaque compresseur sensiblement égales et de préférence dans une fourchette d'environ 10 K,
  • lors de la troisième étape de détente sensiblement isotherme le fluide détendu est refroidit en sortie de chaque turbine pour maintenir les températures du fluide en entrée et en sortie de chaque turbine sensiblement égales et de préférence dans une fourchette d'environ 5 K,
  • les compresseurs et la ou les turbines de détente sont entraînée par au moins un moteur dit à haute vitesse comprenant un arbre de sortie dont l'une des extrémité porte et entraîne en rotation par accouplement direct un premier compresseur et dont l'autre extrémité porte et entraîne en rotation par accouplement direct une turbine de détente et en ce que le procédé comprend une étape de transfert d'une partie du travail mécanique de la ou des turbines vers le ou les compresseurs via le ou les arbres de sortie. En outre, des modes de réalisation de l'invention peuvent comporter l'une ou plusieurs des caractéristiques suivantes :
    • à l'issue de la seconde étape de refroidissement le fluide de travail est amené à une température basse de l'ordre de 60 K et en ce que le circuit de travail comprend un nombre de compresseurs trois fois plus important environ que le nombre de turbines de détente,
    • le fluide de travail est utilisé pour refroidir ou maintenir en froid des éléments supraconducteurs à une température de l'ordre de 65 K,
    • la chute de température du fluide constituant la source froide est sensiblement identique à l'augmentation de température du gaz dans les échangeurs.
The invention further provides a cryogenic refrigeration method for transferring heat from a cold source to a hot source via a working fluid circulating in a closed work circuit, the work circuit comprising in series: a portion of compression comprising at least two compressors arranged in series, a cooling portion of the fluid, an expansion portion comprising at least one expansion turbine, and a heating portion, the process comprising a work cycle comprising a first substantially isothermal compression step fluid in the compression portion by cooling the compressed fluid at the output of the compressors, a second substantially isobaric cooling step of the fluid in the cooling portion, a third step of substantially isothermal expansion of the fluid in the expansion portion by heating the fluid relaxed at the turbine outlet, and a fourth e step of substantially isobaric heating of the fluid having exchanged thermally with the cold source, the working cycle of the fluid (temperature T, entropy S) being of the Ericsson inverser type according to claim 6. Furthermore:
  • during the first substantially isothermal compression step, the compressed fluid is cooled at the outlet of each compressor to maintain the inlet and outlet fluid temperatures of each compressor substantially equal and preferably in a range of about 10 K,
  • during the third substantially isothermal expansion step the expanded fluid is cooled at the outlet of each turbine to maintain the inlet and outlet fluid temperatures of each turbine substantially equal and preferably in a range of about 5 K,
  • the compressors and the expansion turbine or turbines are driven by at least one so-called high speed motor comprising an output shaft whose one end carries and rotates by direct coupling a first compressor and whose other end carries and rotates by direct coupling an expansion turbine and in that the method comprises a step of transferring part of the mechanical work of the turbine or turbines to the compressor or compressors via the output shaft or trees. In addition, embodiments of the invention may include one or more of the following features:
    • at the end of the second cooling step the working fluid is brought to a low temperature of the order of 60 K and in that the work circuit comprises a number of compressors three times larger than the number of turbines of relaxation,
    • the working fluid is used to cool or keep cold superconducting elements at a temperature of the order of 65 K,
    • the temperature drop of the fluid constituting the cold source is substantially identical to the temperature increase of the gas in the exchangers.

L'invention peut présenter l'un ou plusieurs des avantages suivants :

  • le cycle du fluide de travail (type Ericsson inverse) permet d'obtenir un rendement plus important que les systèmes connus sans pour autant créer ou augmenter d'autres inconvénients,
  • le travail de détente dans les turbines peut être avantageusement valorisé,
  • il est possible de s'affranchir de l'utilisation d'huile pour la lubrification ou le refroidissement, ceci permet de supprimer l'installation de déshuilage en aval du compresseur, ainsi que les opérations de traitement et de recyclage des huiles usagées,
  • le système ne nécessite qu'un faible nombre de pièces mobiles ce qui accroît sa simplicité et sa fiabilité. Il est possible grâce à l'invention de s'affranchir pour le compresseur d'une transmission de puissance mécanique du type multiplicateur de vitesse, joints de cardan, ...
  • les opérations de maintenance sont réduites voir pratiquement inexistantes,
  • le système permet d'éviter des joints tournant et d'utiliser un système totalement hermétique vis à vis de l'extérieur. Ceci empêche toute perte ou pollution du gaz de cycle de travail,
  • l'encombrement du réfrigérateur peut être réduit par rapport aux systèmes connus.
The invention may have one or more of the following advantages:
  • the cycle of the working fluid (inverse Ericsson type) makes it possible to obtain a higher yield than the known systems without creating or increasing other disadvantages,
  • the work of relaxation in the turbines can be advantageously valued,
  • it is possible to get rid of the use of oil for lubrication or cooling, this makes it possible to eliminate the de-oiling plant downstream of the compressor, as well as the operations of treatment and recycling of waste oils,
  • the system requires only a small number of moving parts which increases its simplicity and reliability. It is possible thanks to the invention to get rid of the compressor for a mechanical power transmission of the speed multiplier type, cardan joints, ...
  • maintenance operations are reduced or virtually nonexistent,
  • the system avoids rotating joints and uses a totally hermetic system with respect to the outside. This prevents any loss or pollution of the working cycle gas,
  • the size of the refrigerator can be reduced compared to known systems.

D'autres particularités et avantages apparaîtront à la lecture de la description ci-après, faite en référence aux figures dans lesquelles :

  • la figure 1 représente une vue schématique illustrant la structure et le fonctionnement d'un premier exemple de réalisation de dispositif de réfrigération selon l'invention,
  • la figure 2 représente de façon schématique un détail de la figure 1 illustrant un agencement d'un moteur d'entraînement d'un ensemble compresseur-compresseur ou compresseur-turbine,
  • la figure 3 représente de façon schématique un exemple de cycle de travail du fluide de travail du réfrigérateur de la figure 1,
  • la figure 4 représente une vue schématique illustrant la structure et le fonctionnement d'un second exemple de réalisation d'un réfrigérateur selon l'invention,
  • la figure 5 représente de façon schématique un second exemple de cycle de travail du fluide de travail du réfrigérateur selon la figure 3.
Other particularities and advantages will appear on reading the following description, made with reference to the figures in which:
  • the figure 1 represents a schematic view illustrating the structure and operation of a first embodiment of a refrigeration device according to the invention,
  • the figure 2 schematically represents a detail of the figure 1 illustrating an arrangement of a drive motor of a compressor-compressor or compressor-turbine assembly,
  • the figure 3 schematically represents an example of working cycle of the working fluid of the refrigerator of the figure 1 ,
  • the figure 4 represents a schematic view illustrating the structure and operation of a second embodiment of a refrigerator according to the invention,
  • the figure 5 schematically represents a second example of working cycle of the working fluid of the refrigerator according to the figure 3 .

En se référant à l'exemple de réalisation de la figure 1, le réfrigérateur selon l'invention est prévu pour transférer de la chaleur d'une source froide 15 à une température cryogénique vers une source chaude à température ambiante 1 par exemple.Referring to the exemplary embodiment of the figure 1 , the refrigerator according to the invention is provided for transferring heat from a cold source 15 at a cryogenic temperature to a hot source at room temperature 1 for example.

La source froide 15 peut être, par exemple, de l'azote liquide à refroidir et la source chaude 1 de l'eau ou de l'air. Pour réaliser ce transfert de chaleur, le réfrigérateur illustré à la figure 1 utilise un circuit de travail 200 d'un gaz de travail comprenant les composants listés ci-dessous.The cold source 15 may be, for example, liquid nitrogen to be cooled and the hot source 1 of water or air. To achieve this heat transfer, the refrigerator shown in the figure 1 uses a working circuit 200 of a working gas comprising the components listed below.

Le circuit 200 comprend plusieurs compresseurs 3, 5, 7 centrifuges disposés en série et fonctionnant à température ambiante.The circuit 200 comprises a plurality of compressors 3, 5, 7 centrifugals arranged in series and operating at ambient temperature.

Le circuit 200 comprend plusieurs échangeurs de chaleur 2, 4, 6 fonctionnant à température ambiante disposés respectivement à la sortie des compresseurs 3, 5, 7. Les températures du gaz de travail en entrée et en sortie, de chaque étage de compression (c'est-à-dire à l'entrée et à la sortie de chaque compresseur 3, 5, 7), sont maintenues par les échanges thermiques à un niveau sensiblement identique (cf. zone A sur la figure 3 qui représente un cycle de travail du gaz : température en K en fonction de l'entropie S en J/kg). A la figure 3, les parties montantes de la zone A en dents de scie correspondant chacune à un étage de compression tandis que les parties descendantes de cette zone A correspondent chacune à un refroidissement par échangeur.The circuit 200 comprises a plurality of heat exchangers 2, 4, 6 operating at ambient temperature respectively disposed at the output of the compressors 3, 5, 7. The working gas temperatures at the inlet and at the outlet of each compression stage (c ') that is to say at the inlet and the outlet of each compressor 3, 5, 7), are maintained by the heat exchange at a substantially identical level (see zone A on the figure 3 which represents a working cycle of the gas: temperature in K according to the entropy S in J / kg). To the figure 3 , the rising parts of the zone A sawtooth each corresponding to a compression stage while the falling parts of this zone A each correspond to a cooling by exchanger.

Cette disposition permet de se rapprocher d'une compression isotherme. Les températures d'entrée et de sortie, de chaque étage de compression, sont sensiblement les mêmes.This arrangement makes it possible to approach an isothermal compression. The inlet and outlet temperatures of each compression stage are substantially the same.

Les échangeurs 2, 4, 6 peuvent être distincts ou être constitués de portions distinctes d'un même échangeur en échange thermique avec la source chaude 1.The exchangers 2, 4, 6 may be distinct or consist of distinct portions of the same exchanger in heat exchange with the hot source 1.

Le réfrigérateur comprend plusieurs moteurs (70 cf. figure 2) dits à haute vitesse. Par moteur à haute vitesse on désigne habituellement des moteurs dont la vitesse de rotation permet un accouplement direct avec un étage de compression centrifuge ou un étage de détente centripète. Les moteurs 70 à haute vitesse utilisent de préférence des paliers magnétiques ou dynamiques à gaz 171 (figure 2). Un moteur à haute vitesse tourne typiquement à une vitesse de rotation de 10 000 tours par minute ou plusieurs dizaines de milliers de tours par minute. Un moteur basse vitesse tourne plutôt avec une vitesse de quelques milliers de tours par minute.The refrigerator comprises several engines (70 cf. figure 2 ) said at high speed. By high speed motor is usually meant motors whose rotational speed allows direct coupling with a centrifugal compression stage or a centripetal expansion stage. High speed motors 70 preferably use magnetic or dynamic gas bearings 171 ( figure 2 ). A high speed motor typically rotates at a rotational speed of 10,000 rpm or several tens of thousands of revolutions per minute. A low-speed motor runs rather with a speed of a few thousand revolutions per minute.

En aval de la portion de compression comprenant les compresseurs en série, le réfrigérateur comprend un échangeur 8 de chaleur de préférence de type à plaques à contre courant séparant les éléments à température ambiante (en partie haute du circuit 200 représenté à la figure 1) des éléments à température cryogéniques (en partie inférieure du circuit 200). Le fluide est refroidit (correspondant à la zone D de la figure 3). Le refroidissement du gaz de la température ambiante à la température cryogénique s'effectue par échange à contre courant avec le même gaz de travail gaz à température cryogénique qui revient de la portion de détente après échange thermique avec la source froide 15.Downstream of the compression portion comprising the compressors in series, the refrigerator comprises a heat exchanger 8 preferably of plate type against the current separating the elements at room temperature (in the upper part of the circuit 200 shown in FIG. figure 1 ) cryogenic temperature elements (in the lower part of the circuit 200). The fluid is cool (corresponding to zone D of the figure 3 ). The cooling of the gas from room temperature to cryogenic temperature is carried out by countercurrent exchange with the same gas working gas at cryogenic temperature which returns from the expansion portion after heat exchange with the cold source 15.

En aval de cette portion de refroidissement constituée par l'échangeur 8 à plaques, le circuit comporte une ou plusieurs turbines 9, 11, 13 de détente, de préférence de type centripètes, disposées en série. Les turbines 9, 11, 13 fonctionnent à température cryogéniques, les températures d'entrée et de sortie de chaque étage de détente (entrée et sortie de turbine) sont maintenues sensiblement identiques par un ou plusieurs échangeurs de chaleur 10, 12, 14 cryogéniques disposés à la sortie de la ou des turbines. Ceci correspond à la zone C de la figure 3, les portions descendantes de la zone C correspondant chacune à un étage de détente tandis que les portions montantes de cette zone correspondent au réchauffement dans les échangeurs 10, 12, 14. Cette disposition permet de se rapprocher d'une détente isotherme. Les températures d'entrée et de sortie de chaque étage de détente sont sensiblement les mêmes. De plus et afin d'augmenter le rendement du réfrigérateur, l'augmentation de la température du gaz de travail dans le ou les échangeur (10, 12, 14) peut être sensiblement identique (en valeur absolue) à la baisse de la température du fluide à refroidir (15) (source froide).Downstream of this cooling portion constituted by the exchanger 8 with plates, the circuit comprises one or more turbines 9, 11, 13 of expansion, preferably centripetal type, arranged 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 maintained substantially identical by one or more cryogenic heat exchangers 10, 12, 14 disposed at the exit of the turbine or turbines. This corresponds to zone C of the figure 3 , the downward portions of the zone C each corresponding to a relaxation stage while the rising portions of this zone correspond to the heating in the exchangers 10, 12, 14. This arrangement makes it possible to approach an isothermal expansion. The inlet and outlet temperatures of each flash stage are substantially the same. In addition and in order to increase the efficiency of the refrigerator, the increase of the temperature of the working gas in the exchanger or exchangers (10, 12, 14) may be substantially identical (in absolute value) to the decrease in the temperature of the refrigerator. fluid to be cooled (15) (cold source).

Ces échangeurs 10, 12, 14 de réchauffement peuvent être distincts ou être constitués de portions distinctes d'un même échangeur en échange thermique avec la source froide 15.These heat exchangers 10, 12, 14 may be distinct or consist of separate portions of the same exchanger in heat exchange with the cold source 15.

En aval de la portion de détente et de l'échange thermique avec la source froide 15, le fluide de travail échange thermiquement à nouveau avec l'échangeur 8 de chaleur à plaques (zone B de la figure 3). Le fluide échange thermiquement dans l'échangeur 8 à contre courant par rapport à son passage après la portion de compression. Après réchauffage le fluide revient dans la portion de compression et peut recommencer un cycle.Downstream of the expansion portion and the heat exchange with the cold source 15, the working fluid thermally exchanges again with the heat exchanger 8 plates (zone B of the figure 3 ). The fluid thermally exchanges in the exchanger 8 against the current relative to its passage after the compression portion. After reheating the fluid returns to the compression portion and can start a cycle again.

Le circuit peut comprendre en outre une capacité de gaz de travail à température ambiante (non représentée par soucis de simplification) pour limiter la pression dans les circuits, lors de l'arrêt du réfrigérateur par exemple.The circuit may further comprise a working gas capacity at room temperature (not shown for the sake of simplification) to limit the pressure in the circuits, during the stopping of the refrigerator for example.

Le réfrigérateur utilise de préférence comme fluide de travail un fluide en phase gazeuse circulant en circuit fermé. Celui-ci est constitué par exemple d'un gaz pur ou d'un mélange de gaz pur. Les gaz les mieux adaptés à cette technologie sont notamment : l'hélium, le néon, l'azote, l'oxygène et l'argon. Le monoxyde de carbone et le méthane peuvent également être utilisés.The refrigerator preferably uses as a working fluid a gas phase fluid circulating in a closed circuit. This consists for example of a pure gas or a mixture of pure gas. The gases best suited to this technology include: helium, neon, nitrogen, oxygen and argon. Carbon monoxide and methane can also be used.

Le réfrigérateur est conçu et piloté ainsi de façon à obtenir un cycle de travail du fluide se rapprochant du cycle d'Ericsson inverse. C'est à dire: une compression isotherme, un refroidissement isobare, une détente isotherme et un réchauffement isobare.The refrigerator is designed and controlled so as to obtain a working cycle of the fluid approaching the reverse Ericsson cycle. That is: isothermal compression, isobaric cooling, isothermal expansion and isobaric heating.

Selon une particularité avantageuse le réfrigérateur utilise pour l'entraînement au moins des compresseurs 3, 5, 7 (c'est-à-dire pour l'entraînement des roues des compresseurs) plusieurs moteurs 70 dits à hautes vitesses.According to an advantageous feature the refrigerator uses for the drive at least compressors 3, 5, 7 (that is to say, for driving the wheels of the compressors) several motors 70 said to high speeds.

Comme schématisé à la figure 2, chaque moteur 70 à haute vitesse reçoit sur une des extrémités de son arbre de sortie une roue de compresseur 31 et, sur l'autre extrémité de son arbre une autre roue de compresseur ou une roue de turbine 9. Cette disposition procure de nombreux avantages. Cette configuration permet dans le réfrigérateur un accouplement direct entre le moteur 70 et les roues de compresseur 3, 5, 7 ou entre le moteur 70 et les roues des turbines 9, 11, 13. Ceci permet de s'affranchir d'un multiplicateur ou réducteur de vitesse (ce qui limite le nombre de pièces mobiles nécessaires). Cette configuration permet également une valorisation du travail mécanique de la ou des turbines 9, 11, 13 et par conséquent une augmentation du rendement énergétique global du réfrigérateur. Selon cette configuration, le réfrigérateur a un fonctionnement sans huile, ce qui permet de garantir la pureté du gaz de travail et supprime la nécessitée d'une opération de déshuilage.As schematized at figure 2 , each high-speed motor 70 receives on one end of its output shaft a compressor wheel 31 and, on the other end of its shaft, another compressor wheel or a turbine wheel 9. This arrangement provides numerous advantages . This configuration allows in the refrigerator a direct coupling between the motor 70 and the compressor wheels 3, 5, 7 or between the motor 70 and the wheels of the turbines 9, 11, 13. This makes it possible to overcome a multiplier or speed reducer (which limits the number of moving parts required). This configuration also allows a valuation of the mechanical work of the turbine or turbines 9, 11, 13 and therefore an increase in the overall energy efficiency of the refrigerator. According to this configuration, the refrigerator has an oil-free operation, which ensures the purity of the working gas and eliminates the need for a de-oiling operation.

Le nombre de moteur à haute vitesse est principalement fonction du rendement énergétique souhaité pour le réfrigérateur. Plus ce rendement est important, plus le nombre de moteur haute vitesse doit être élevé.The number of high speed engines is mainly a function of the desired energy efficiency for the refrigerator. The higher this efficiency, the higher the number of high speed motors.

Le rapport entre le nombre d'étage de compression (compresseurs) et le nombre d'étages de détente (turbines) est fonction de la température froide cible. Par exemple, pour un réfrigérateur dont la source froide est à 273 K, le nombre d'étage de compression sera sensiblement égal au nombre d'étage de détente. Pour un réfrigérateur dont la source froide est à 65 K, le nombre d'étage de compression est environ 3 fois plus important que le nombre d'étage de détente.The ratio between the number of compression stage (compressors) and the number of expansion stages (turbines) is a function of the target cold temperature. For example, for a refrigerator whose cold source is 273 K, the number of compression stage will be substantially equal to the number of stage of relaxation. For a refrigerator with a cold source of 65 K, the number of compression stages is approximately 3 times greater than the number of stages of expansion.

La figure 4 illustre un autre mode de réalisation qui peut par exemple être utilisé pour refroidir ou maintenir en température des câbles supraconducteurs à une température cryogénique d'environ 65 K. Pour ce niveau de température, le nombre d'étage de compression (compresseurs) doit être environ trois fois plus important que le nombre d'étages de détente (turbines). Ceci peut être réalisé selon plusieurs configurations possibles. Par exemple trois compresseurs et une turbine ou six compresseurs et deux turbines,...The figure 4 illustrates another embodiment which can for example be used to cool or maintain superconducting cables at a cryogenic temperature of about 65 K. At this temperature level, the number of compression stages (compressors) must be approximately three times more than the number of stages of relaxation (turbines). This can be done according to several possible configurations. For example three compressors and a turbine or six compressors and two turbines, ...

Le choix du nombre d'organe sera fonction du rendement énergétique souhaité. Ainsi, une solution utilisant trois compresseurs et une turbine aura un rendement énergétique moins important qu'une solution utilisant six compresseurs et deux turbines.The choice of the number of organs will depend on the desired energy efficiency. Thus, a solution using three compressors and a turbine will have a lower energy efficiency than a solution using six compressors and two turbines.

Dans l'exemple de la figure 4 le réfrigérateur comprend six compresseurs 101, 102, 103, 104, 105, 106 et deux turbines 116, 111 et quatre moteurs à haute vitesse 107, 112, 114, 109. Les deux premiers compresseurs 101, 102 (c'est-à-dire les roues des compresseurs) sont montés respectivement aux deux extrémités d'un premier moteur haute vitesse 107. Les deux compresseurs 103, 104 suivants sont montés respectivement aux deux extrémités d'un second moteur haute vitesse 112. Le compresseur suivant 105 et la turbine 116 (c'est-à-dire la roue de la turbine) sont montés respectivement aux deux extrémités d'un troisième moteur haute vitesse 114. Enfin, la dernière turbine 111 et le sixième compresseur 106 sont montés respectivement aux deux extrémités d'un quatrième moteur 109.In the example of the figure 4 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 (i.e. the compressor wheels) are respectively mounted at both ends of a first high-speed motor 107. The two following compressors 103, 104 are respectively mounted at the two ends of a second high-speed motor 112. The following compressor 105 and the turbine 116 (that is to say the wheel of the turbine) are respectively mounted at both ends of a third high-speed motor 114. Finally, the last turbine 111 and the sixth compressor 106 are mounted respectively at both ends of a fourth engine 109.

Le cheminement du gaz de travail lors d'un cycle dans le circuit en boucle fermée peut être décrit comme suit.The flow of the working gas during a cycle in the closed loop circuit can be described as follows.

Lors d'une première étape le gaz est comprimé progressivement en passant successivement dans les quatre compresseurs en série 101, 102, 103, 104, 105, 106.In a first step the gas is gradually compressed by passing successively in the four series compressors 101, 102, 103, 104, 105, 106.

A l'issue de chaque étage de compression (à la sortie de chaque compresseur) le gaz de travail est refroidi dans un échangeur de chaleur respectif 108 (par échange thermique avec de l'air ou de l'eau par exemple) pour se rapprocher d'une compression isotherme. Après cette portion de compression le gaz est refroidi de façon isobare au travers d'un échangeur à plaques à contre-courant 103. Après cette portion de refroidissement, le gaz de refroidissement est détendu progressivement dans les deux turbines centripètes en série 116, 111. Après chaque étage de détente le gaz de travail est réchauffé par échange thermique dans un échangeur 110 (par exemple par échange thermique avec la source froide), de façon à réaliser une détente sensiblement isotherme. A l'issue de cette détente isotherme le gaz de travail est réchauffé dans l'échangeur 113 et peut ensuite recommencer un nouveau cycle par une compression.At the end 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 get closer an isothermal compression. After this portion of compression the 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 series centripetal turbines 116, 111. After each expansion stage the working gas is heated by heat exchange in an exchanger 110 (for example by heat exchange with the cold source), so as to achieve a substantially isothermal expansion. At the end of this isothermal expansion, the working gas is reheated in the exchanger 113 and can then start a new cycle again by compression.

La figure 5 représente le cycle (température T et entropie S) du fluide de travail du réfrigérateur de la figure 5. Comme précédemment pour la figure 3, on distingue dans la zone A de compression six dents de scie correspondant aux six compressions et refroidissements successifs. Dans la zone C de détente on reconnaît deux dents de scie correspondant aux deux détentes et réchauffement successifs.The figure 5 represents the cycle (temperature T and entropy S) of the working fluid of the refrigerator of the figure 5 . As previously for the figure 3 in the compression zone A, there are six sawtooths corresponding to the six successive compressions and coolings. In zone C of relaxation we recognize two sawtooth corresponding to two successive relaxation and warming.

L'invention améliore les réfrigérateurs cryogéniques en terme de rendement énergétique, de fiabilité et d'encombrement. L'invention permet de diminuer les opérations de maintenance et de supprimer l'utilisation d'huiles.The invention improves cryogenic refrigerators in terms of energy efficiency, reliability and size. The invention makes it possible to reduce the maintenance operations and to eliminate the use of oils.

Bien entendu l'une ou les deux extrémités des arbres de sortie du ou des moteurs peuvent entraîner directement plus d'une route (c'est-à-dire plusieurs compresseurs ou plusieurs turbines).Of course, one or both ends of the output shafts of the motor (s) can directly drive more than one road (ie several compressors or several turbines).

Claims (9)

  1. Cryogenic refrigeration device intended to transfer the heat from a cold source (15) to a hot source (1) via a working fluid circulating in a closed working circuit (200), the working circuit (200) comprising in series: a substantially isothermal fluid compression section, a substantially isobar fluid cooling section, a substantially isothermal fluid expansion section and a substantially isobar fluid heating section, the compression section of the working circuit (200) comprising at least two compressors (7, 5, 3, 101, 102, 103, 104, 105, 106) arranged in series and at least one compressed fluid cooling exchanger (6, 4, 2, 108) arranged at the outlet of each compressor (7, 5, 3, 101, 102, 103, 104, 105, 106), the expansion section of the working circuit (200) comprising at least one expansion turbine (9, 11, 13, 116, 111) and at least one expanded fluid heating exchanger (10, 12, 14, 110), characterised in that the compressors (7, 5, 3, 101, 102, 103, 104, 105, 106) and the expansion turbine(s) (9, 11, 13) is/are driven by several motors (70, 107, 112, 114, 109) called high-speed motors, in other words, rotating at a speed of 10000 rotations per minute, or several tens of thousands of rotations per minute, and of which at least one of the motors comprises an output shaft, of which one of the ends supports and rotates by direct coupling, a first compressor (7, 5, 3, 101, 102, 103, 104, 105, 106) and of which the other end supports and rotates by direct coupling, a expansion turbine (9, 11, 13, 116, 111), the number of compression levels, in other words compressors, being substantially equal to or more than the number of expansion levels, in other words turbines, and in that the compressors (7, 5, 3, 101, 102, 103, 104, 105, 106) are of the centrifugal compression type, and in that the expansion turbine(s) (9, 11, 13, 116, 111) is/are of the centripetal expansion type, and in that the output shafts (71) of the motors (70, 107, 112, 114, 109) are assembled on the magnetic-type or gas-activated-type bearings (171), said bearings (171) being used for sustaining the compressors (7, 5, 3, 101, 102, 103, 104, 105, 106) and the turbines (9, 11, 13, 116, 111), and in that the cooling section and the heating section comprise a shared heat exchanger (8, 113) wherein the working fluid passes through at counter-current depending on if it is cooled or heated.
  2. Device according to claim 1, characterised in that the working circuit comprises a volume forming a buffer capacity for storing the working fluid.
  3. Device according to claim 1 or 2, characterised in that the working fluid is in gaseous phase and constituted by a pure gas or a mixture of pure gases among: helium, neon, nitrogen, oxygen, argon, carbon monoxide, methane, or any other fluid that has a gaseous phase at the temperature of the cold source.
  4. Device according to any one of claims 1 to 3, characterised in that it comprises at least one motor (70, 107, 112, 114, 109) of which at least one of the ends of the output shaft rotates by direct coupling, at least two wheels (compressor wheels and/or turbine wheels).
  5. Device according to claim 4, characterised in that it comprises at least one motor of which one end of the output shaft thereof rotates by direct coupling, two compressor wheels, the other end of the output shaft rotates by direct coupling, one turbine wheel.
  6. Method of cryogenic refrigeration intended to transfer the heat from a cold source (15) to a hot source (1) via a working fluid circulating in a closed working circuit (200), the working circuit (200) comprising in series: a compression section comprising at least two compressors (7, 5, 3, 101, 102, 103, 104, 105, 106) arranged in series, a fluid cooling section, a expansion section comprising at least one expansion turbine (9, 11, 13, 116, 111), and a heating section, the method comprising a working cycle comprising a first substantially isothermal fluid compression step in the compression section by cooling the compressed fluid exiting the compressors (7, 5, 3, 101, 102, 103, 104, 105, 106), a second substantially isobar fluid compression step in the cooling section, a third substantially isothermal fluid expansion step in the expansion portion by heating the expanded fluid exiting the turbine, and a fourth substantially isobar fluid heating step having thermally exchanged with the cold source (15), the fluid working cycle (temperature T, entropy S) being of the opposite Ericsson type, during the first substantially isothermal compression step, the compressed fluid is cooled exiting each compressor (7, 5, 3, 101, 102, 103, 104, 105, 106) to keep the fluid temperatures entering and exiting each compressor substantially equal, and preferably in a range of around 10K, during the third substantially isothermal expansion step, the expanded fluid being heated exiting each turbine (9, 11, 13, 116, 111) to keep the fluid temperatures entering and exiting each turbine (9, 11, 13, 116, 111) substantially equal, and preferably in a range of around 5K, characterised in that the compressors (7, 5, 3, 101, 102, 103, 104, 105, 106) and the expansion turbine(s) (9, 11, 13, 116, 111) is/are driven by several motors (70, 107, 112, 114, 109) called high-speed motors, in other words, rotating at a speed of 10000 rotations per minutes or several tens of thousands of rotations per minutes, and of which at least one of the motors comprises an output shaft of which one of the ends supports and rotates by direct coupling, a first compressor (7, 5, 3, 101, 102, 103, 104, 105, 106) and of which the other end supports and rotates by direct coupling, a expansion turbine (9, 11, 13, 116, 111), the number of compression steps, in other words compressors, being substantially equal to or more than the number of expansion steps, in other words turbines, and in that the method comprises a step of transferring from one part of the mechanical working of the turbine(s) (9, 11, 13, 116, 111) to the compressor(s) (7, 5, 3, 101, 102, 103, 104, 105, 106) via the output shaft(s) (71), and in that the output shafts (71) of the motors (70, 107, 112, 114, 109) are assembled on the magnetic-type or gas-activation-type bearings (171), said bearings (171) being used for sustaining the compressors and turbines, and in that the cooling section and the heating section comprise a shared heat exchanger (8, 113) wherein the working fluid passes through at counter-current depending on if it is cooled or heated.
  7. Method according to claim 6, characterised in that from the second cooling step, the working fluid is brought to a low temperature of around 60K and in that the working circuit (200) comprises a number of compressors (7, 5, 3, 101, 102, 103, 104, 105, 106) that is three times the amount the number of expansion turbines (9, 11, 13, 116, 111).
  8. Method according to any one of claims 6 or 7, characterised in that the working fluid is used for cooling or keeping cold the superconductor elements at a temperature of around 65K.
  9. Method according to any one of claims 6 to 8, characterised in that the fall in temperature of the fluid constituting the cold source (15) is substantially identical to the increase in temperature of the working gas in the heat exchangers (110, 10, 12, 14) of the working circuit (200).
EP08852903.7A 2007-11-23 2008-10-23 Cryogenic refrigeration method and device Active EP2225501B2 (en)

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PL08852903.7T PL2225501T5 (en) 2007-11-23 2008-10-23 Cryogenic refrigeration method and device
EP19174805.2A EP3561411A1 (en) 2007-11-23 2008-10-23 Device and method for cryogenic refrigeration
EP18178529.6A EP3410035A1 (en) 2007-11-23 2008-10-23 Device and method for cryogenic refrigeration

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FR0759243A FR2924205B1 (en) 2007-11-23 2007-11-23 CRYOGENIC REFRIGERATION DEVICE AND METHOD
PCT/FR2008/051919 WO2009066044A2 (en) 2007-11-23 2008-10-23 Cryogenic refrigeration method and device

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EP18178529.6A Division-Into EP3410035A1 (en) 2007-11-23 2008-10-23 Device and method for cryogenic refrigeration
EP18178529.6A Division EP3410035A1 (en) 2007-11-23 2008-10-23 Device and method for cryogenic refrigeration

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DK2225501T3 (en) 2018-11-19
ES2693066T5 (en) 2025-04-21
DK2225501T4 (en) 2025-03-10
FR2924205A1 (en) 2009-05-29
PL2225501T5 (en) 2025-04-28
EP2225501A2 (en) 2010-09-08
EP2225501B2 (en) 2025-01-15
HUE040042T2 (en) 2019-02-28
ES2693066T3 (en) 2018-12-07
FI2225501T4 (en) 2025-03-17
CN101868677B (en) 2012-10-03
US20100263405A1 (en) 2010-10-21
EP3410035A1 (en) 2018-12-05
WO2009066044A2 (en) 2009-05-28
JP2011504574A (en) 2011-02-10
WO2009066044A3 (en) 2009-07-16
CN101868677A (en) 2010-10-20
KR20100099129A (en) 2010-09-10
FR2924205B1 (en) 2013-08-16
WO2009066044A4 (en) 2009-09-11
EP3561411A1 (en) 2019-10-30

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