EP2225501B2 - Kryogenes kühlverfahren und entsprechende vorrichtung - Google Patents

Kryogenes kühlverfahren und entsprechende vorrichtung Download PDF

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Publication number
EP2225501B2
EP2225501B2 EP08852903.7A EP08852903A EP2225501B2 EP 2225501 B2 EP2225501 B2 EP 2225501B2 EP 08852903 A EP08852903 A EP 08852903A EP 2225501 B2 EP2225501 B2 EP 2225501B2
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EP
European Patent Office
Prior art keywords
fluid
expansion
compressors
working
section
Prior art date
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EP08852903.7A
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English (en)
French (fr)
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EP2225501A2 (de
EP2225501B1 (de
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 EP18178529.6A priority Critical patent/EP3410035A1/de
Priority to EP19174805.2A priority patent/EP3561411A1/de
Priority to PL08852903.7T priority patent/PL2225501T5/pl
Publication of EP2225501A2 publication Critical patent/EP2225501A2/de
Publication of EP2225501B1 publication Critical patent/EP2225501B1/de
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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
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    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—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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    • F25J1/0072—Nitrogen
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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
    • 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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    • 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
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    • 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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    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • 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.
    • F25J1/0281—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
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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
    • F25J1/0287—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings including an electrical motor
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    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0285—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings
    • 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 
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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 intended to transfer 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 compression portion, a cooling portion, an expansion portion and a heating portion.
  • the cold source can be, for example, liquid nitrogen to be cooled and the hot source water or air.
  • Known refrigerators for cooling superconducting elements generally use a reverse Brayton cycle. These known refrigerators use a lubricated screw compressor, a plate counterflow exchanger and 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 makes it possible to avoid any risk of leakage.
  • the entire system is in fact hermetic and does not include any rotating seal with respect to the atmosphere (such as mechanical seals or "dry face seals").
  • the refrigerator according to the invention is designed to transfer heat from a cold source 15 at a cryogenic temperature to a hot source at a temperature ambient 1 for example.
  • the cold source 15 can be, for example, liquid nitrogen to be cooled and the hot source 1 can be water or air.
  • the refrigerator illustrated in figure 1 uses a working circuit 200 of a working gas comprising the components listed below.
  • Circuit 200 comprises several centrifugal compressors 3, 5, 7 arranged in series and operating at room temperature.
  • the circuit 200 comprises several heat exchangers 2, 4, 6 operating at ambient temperature arranged 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 i.e. at the inlet and outlet of each compressor 3, 5, 7) are maintained by the heat exchanges at a substantially identical level (see zone A on the figure 3 which represents a gas work cycle: temperature in K as a function of the entropy S in J/kg).
  • zone A on the figure 3 which represents a gas work cycle: temperature in K as a function of the entropy S in J/kg.
  • the exchangers 2, 4, 6 may be separate or consist of separate portions of the same exchanger in heat exchange with the hot source 1.
  • the refrigerator includes several motors (70 cf. figure 2 ) so-called high-speed motors.
  • High-speed motors are usually motors whose rotation 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 runs at a rotational speed of 10,000 revolutions per minute or several tens of thousands of revolutions per minute.
  • a low-speed motor typically runs at 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 the counter-current plate type 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 cooled (corresponding to zone D of the figure 3 ).
  • the cooling of the gas from ambient temperature to cryogenic temperature is carried out by countercurrent exchange with the same 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 plate exchanger 8, the circuit comprises one or more expansion turbines 9, 11, 13, preferably of the centripetal type, arranged in series.
  • the turbines 9, 11, 13 operate at cryogenic temperatures, 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 arranged 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 exchangers 10, 12, 14.
  • This arrangement makes it possible to approach an isothermal expansion.
  • the inlet and outlet temperatures of each expansion stage are substantially the same.
  • the increase in the temperature of the working gas in the 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).
  • heating exchangers 10, 12, 14 may be separate or consist of separate portions of the same exchanger in heat exchange with the cold source 15.
  • the working fluid exchanges heat again with the plate heat exchanger 8 (zone B of the figure 3 ).
  • the fluid exchanges heat in the exchanger 8 in counter-current with respect 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 include a capacity for working gas at ambient temperature (not shown for the sake of simplification) to limit the pressure in the circuits, when the refrigerator is switched off for example.
  • the refrigerator preferably uses a gaseous phase fluid circulating in a closed circuit as the working fluid.
  • a gaseous phase fluid circulating in a closed circuit as the working fluid.
  • This consists, for example, of a pure gas or a mixture of pure gases.
  • 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 in such a way as to obtain a fluid work cycle approaching the reverse Ericsson cycle. That is to say: isothermal compression, isobaric cooling, isothermal expansion and isobaric heating.
  • the refrigerator uses several so-called high-speed motors 70 for driving at least the compressors 3, 5, 7 (i.e. for driving the compressor wheels).
  • each high-speed 70 engine 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 many 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 dispense with a speed multiplier or reducer (which limits the number of moving parts required).
  • This configuration also allows an enhancement of the mechanical work of the turbine(s) 9, 11, 13 and consequently an increase in the overall energy efficiency of the refrigerator.
  • the refrigerator has an oil-free operation, which makes it possible to guarantee the purity of the working gas and eliminates the need for a de-oiling operation.
  • the number of high-speed motors is mainly a function of the desired energy efficiency of the refrigerator. The higher the efficiency, the higher the number of high-speed motors should be.
  • the ratio between the number of compression stages (compressors) and the number of expansion stages (turbines) is a function of the target cold temperature. For example, for an unclaimed refrigerator with a cold source at 273 K, the number of compression stages will be substantially equal to the number of expansion stages. For a refrigerator with a cold source at 65 K, the number of compression stages is approximately 3 times greater than the number of expansion stages.
  • FIG. 4 illustrates another embodiment which can for example be used to cool or maintain the temperature of superconducting cables at a cryogenic temperature of about 65 K.
  • the number of compression stages compressors
  • turbines the number of expansion stages (turbines). This can be achieved 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 i.e., the compressor wheels
  • the next two compressors 103, 104 are respectively mounted at both ends of a second high-speed motor 112.
  • the next compressor 105 and the turbine 116 i.e., the turbine wheel
  • the last turbine 111 and the sixth compressor 106 are respectively mounted at both ends of a fourth motor 109.
  • the path of the working gas during a cycle in the closed loop circuit can be described as follows.
  • the gas is compressed progressively by passing successively through the four compressors in series 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 approach an isothermal compression.
  • the gas is cooled isobarically through a counter-current plate exchanger 103.
  • the cooling gas is gradually expanded in the two centripetal turbines in series 116, 111.
  • the working gas is reheated 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 by compression.
  • FIG 5 represents the cycle (temperature T and entropy S) of the working fluid of the refrigerator of the figure 5 .
  • compression zone A we can see six saw teeth corresponding to the six successive compressions and coolings.
  • relaxation zone C we can see two saw teeth corresponding to the two successive relaxations and heatings.
  • the invention improves cryogenic refrigerators in terms of energy efficiency, reliability and size.
  • the invention makes it possible to reduce maintenance operations and eliminate the use of oils.
  • one or both ends of the output shafts of the engine(s) can directly drive more than one route (i.e. multiple compressors or multiple turbines).

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Claims (7)

  1. Kryogene Kühlvorrichtung, die dazu bestimmt ist, über ein Arbeitsfluid, das in einem geschlossenen Arbeitskreislauf (200) zirkuliert, Wärme von einer kalten Quelle (15) zu einer heißen Quelle (1) zu übertragen,
    wobei der Arbeitskreislauf (200) seriell Folgendes umfasst:
    einen im Wesentlichen isothermen Kompressionsabschnitt des Fluids, einen im Wesentlichen isobaren Kühlabschnitt des Fluids,
    einen im Wesentlichen isothermen Expansionsabschnitt des Fluids und einen im Wesentlichen isobaren Erwärmungsabschnitt des Fluids,
    wobei der Kompressionsabschnitt des Arbeitskreislaufs (200) mindestens zwei seriell angeordnete Kompressoren (7, 5, 3, 101, 102, 103, 104, 105, 106) und mindestens einen am Ausgang jedes Kompressors (7, 5, 3, 101, 102, 103, 104, 105, 106) angeordneten Tauscher (6, 4, 2, 108) zum Kühlen des komprimierten Fluids umfasst,
    wobei der Expansionsabschnitt des Arbeitskreislaufs (200) mindestens eine Expansionsturbine (9, 11, 13, 116, 111) und mindestens einen Tauscher (10, 12, 14, 110) zum Erwärmen des expandierten Fluids umfasst,
    wobei die Kompressoren (7, 5, 3, 101, 102, 103, 104, 105, 106) und die Entspannungsturbine(n) (9, 11, 13) von mehreren sogenannten Hochgeschwindigkeitsmotoren (70, 107, 112, 114, 109) angetrieben werden, die mit einer Drehzahl von 10.000 Umdrehungen pro Minute oder mehreren Zehntausend Umdrehungen pro Minute rotieren,
    wobei jeder Motor eine Abtriebswelle umfasst, deren eines Ende einen ersten Kompressor (7, 5, 3, 101, 102, 103, 104, 105, 106) trägt und durch direkte Kopplung in Rotation versetzt und deren anderes Ende einen zweiten Kompressor oder eine Expansionsturbine (9, 11, 13, 116, 111) trägt und durch direkte Kopplung in Rotation versetzt,
    wobei die Kompressoren (7, 5, 3, 101, 102, 103, 104, 105, 106) vom Typ der Zentrifugalkompression sind,
    wobei die Expansionsturbine(n) (9, 11, 13, 116, 111) vom Typ der Zentripetalexpansion sind,
    wobei die Abtriebswellen (71) der Motoren (70, 107, 112, 114, 109) auf Lagern (171) vom magnetischen oder gasdynamischen Typ montiert sind,
    wobei die Lager (171) zur Abstützung der Kompressoren (7, 5, 3, 101, 102, 103, 104, 105, 106) und der Turbine(n) (9, 11, 13, 116, 111) verwendet werden,
    wobei der Kühlabschnitt und der Erwärmungsabschnitt einen gemeinsamen Wärmetauscher (8, 113) umfassen, in dem das Arbeitsfluid in Abhängigkeit davon, ob es gekühlt oder erwärmt wird, im Gegenstrom fließt,
    dadurch gekennzeichnet, dass die Anzahl der Kompressionsstufen, d. h. der Kompressoren, größer ist als die Anzahl der Expansionsstufen, d. h. der seriell angeordneten Kompressoren.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der Arbeitskreislauf ein Volumen umfasst, das eine Pufferkapazität zur Speicherung des Arbeitsfluids bildet.
  3. Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass sich das Arbeitsfluid in der Gasphase befindet und aus einem reinen Gas oder einem Gemisch aus reinen Gasen aus: Helium, Neon, Stickstoff, Sauerstoff, Argon, Kohlenmonoxid, Methan, oder einem anderen Fluid, das bei der Temperatur der kalten Quelle eine Gasphase aufweist, gebildet ist.
  4. Kryogenes Kühlverfahren, das dazu bestimmt ist, über ein Arbeitsfluid, das in einem geschlossenen Arbeitskreislauf (200) zirkuliert, Wärme von einer kalten Quelle (15) zu einer heißen Quelle (1) zu übertragen,
    wobei der Arbeitskreislauf (200) seriell Folgendes umfasst:
    einen Kompressionsabschnitt, der mindestens zwei seriell angeordnete Kompressoren (7, 5, 3, 101, 102, 103, 104, 105, 106) umfasst,
    einen Kühlabschnitt des Fluids, einen Expansionsabschnitt, der mindestens eine Expansionsturbine (9, 11, 13, 116, 111) umfasst, und einen Erwärmungsabschnitt,
    wobei das Verfahren einen Arbeitszyklus umfasst, der folgende Schritte beinhaltet:
    einen ersten Schritt der im Wesentlichen isothermen Kompression des Fluids im Kompressionsabschnitt durch Kühlen des komprimieren Fluids am Ausgang der Kompressoren (7, 5, 3, 101, 102, 103, 104, 105, 106), einen zweiten Schritt der im Wesentlichen isobaren Kühlung des Fluids im Kühlabschnitt,
    einen dritten Schritt der im Wesentlichen isothermen Expansion des Fluids im Expansionsabschnitt durch Erwärmen des expandierten Fluids am Ausgang der Turbine(n) und
    einen vierten Schritt der im Wesentlichen isobaren Erwärmung des Fluids, das mit der kalten Quelle (15) Wärme ausgetauscht hat,
    wobei der Arbeitszyklus des Fluids (Temperatur T, Entropie S) während des ersten Schritts der im Wesentlichen isothermen Kompression vom inversen Ericsson-Typ ist,
    wobei das komprimierte Fluid am Ausgang jedes Kompressors (7, 5, 3, 101, 102, 103, 104, 105, 106) gekühlt wird, um die Temperaturen des Fluids am Eingang und am Ausgang jedes Kompressors im Wesentlichen gleich und vorzugsweise in einem Bereich von etwa 10 K zu halten,
    wobei während des dritten Schritts der im Wesentlichen isothermen Expansion das expandierte Fluid am Ausgang jeder Turbine (9, 11, 13, 116, 111) erwärmt wird, um die Temperaturen des Fluids am Eingang und am Ausgang jeder Turbine (9, 11, 13, 116, 111) im Wesentlichen in einem Bereich von etwa 5 K gleich zu halten,
    wobei die Kompressoren (7, 5, 3, 101, 102, 103, 104, 105, 106) und die Expansionsturbine(n) (9, 11, 13, 116, 111) von mehreren sogenannten Hochgeschwindigkeitsmotoren (70, 107, 112, 114, 109) angetrieben werden, die mit einer Drehzahl von 10.000 Umdrehungen pro Minute oder mehreren Zehntausend Umdrehungen pro Minute rotieren,
    wobei jeder Motor eine Abtriebswelle umfasst, deren eines Ende einen ersten Kompressor (7, 5, 3, 101, 102, 103, 104, 105, 106) trägt und durch direkte Kopplung in Rotation versetzt und deren anderes Ende einen Kompressor oder eine Expansionsturbine (9, 11, 13, 116, 111) trägt und durch direkte Kopplung in Rotation versetzt,
    wobei das Verfahren einen Schritt umfasst, bei dem ein Teil der mechanischen Arbeit der Turbine(n) (9, 11, 13, 116, 111) über die Abtriebswelle(n) (71) auf den Kompressor bzw. die Kompressoren (7, 5, 3, 101, 102, 103, 104, 105, 106) übertragen wird,
    wobei die Abtriebswellen (71) der Motoren (70, 107, 112, 114, 109) auf Lagern (171) vom magnetischen oder gasdynamischen Typ montiert sind,
    wobei die Lager (171) zur Abstützung der Kompressoren und Turbinen verwendet werden,
    wobei der Kühlabschnitt und der Erwärmungsabschnitt einen gemeinsamen Wärmetauscher (8, 113) umfassen, in dem das Arbeitsfluid in Abhängigkeit davon, ob es gekühlt oder erwärmt wird, im Gegenstrom fließt, wobei die Anzahl der Kompressionsstufen, d. h. der Kompressoren, größer ist als die Anzahl der Expansionsstufen, d. h. der Turbinen.
  5. Verfahren nach Anspruch 4, dadurch gekennzeichnet, dass am Ende des zweiten Schritts des Kühlens das Arbeitsfluid auf eine niedrige Temperatur im Bereich von etwa 60 K gebracht wird, und dadurch, dass der Arbeitskreislauf (200) eine Anzahl von Kompressoren (7, 5, 3, 101, 102, 103, 104, 105, 106) umfasst, die dreimal so groß wie die Anzahl der Expansionsturbinen (9, 11, 13, 116, 111) ist.
  6. Verfahren nach einem der Ansprüche 4 oder 5, dadurch gekennzeichnet, dass das Arbeitsfluid zum Kühlen oder Kühlhalten von supraleitenden Elementen auf eine(r) Temperatur im Bereich von 65 K verwendet wird.
  7. Verfahren nach einem der Ansprüche 4 bis 6, dadurch gekennzeichnet, dass der Temperaturabfall des Fluids, das die kalte Quelle (15) bildet, im Wesentlichen gleich dem Temperaturanstieg des Arbeitsgases in den Wärmetauschern (110, 10, 12, 14) des Arbeitskreislaufs (200) ist.
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EP3561411A1 (de) 2019-10-30
HUE040042T2 (hu) 2019-02-28
WO2009066044A4 (fr) 2009-09-11
FI2225501T4 (fi) 2025-03-17
FR2924205B1 (fr) 2013-08-16
ES2693066T5 (en) 2025-04-21
CN101868677A (zh) 2010-10-20
ES2693066T3 (es) 2018-12-07
WO2009066044A3 (fr) 2009-07-16
WO2009066044A2 (fr) 2009-05-28
EP2225501A2 (de) 2010-09-08
PL2225501T5 (pl) 2025-04-28
PL2225501T3 (pl) 2019-02-28
EP3410035A1 (de) 2018-12-05
DK2225501T3 (en) 2018-11-19
US20100263405A1 (en) 2010-10-21
FR2924205A1 (fr) 2009-05-29
EP2225501B1 (de) 2018-09-05
DK2225501T4 (da) 2025-03-10
KR20100099129A (ko) 2010-09-10
JP2011504574A (ja) 2011-02-10
CN101868677B (zh) 2012-10-03

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