EP4361527A1 - Cryoréfrigérateur et procédé de fonctionnement de cryoréfrigérateur - Google Patents

Cryoréfrigérateur et procédé de fonctionnement de cryoréfrigérateur Download PDF

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Publication number
EP4361527A1
EP4361527A1 EP23202568.4A EP23202568A EP4361527A1 EP 4361527 A1 EP4361527 A1 EP 4361527A1 EP 23202568 A EP23202568 A EP 23202568A EP 4361527 A1 EP4361527 A1 EP 4361527A1
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EP
European Patent Office
Prior art keywords
pressure
cryocooler
cold heads
cold
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP23202568.4A
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German (de)
English (en)
Inventor
Shuji Oyama
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Sumitomo Heavy Industries Ltd
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Sumitomo Heavy Industries Ltd
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Filing date
Publication date
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Publication of EP4361527A1 publication Critical patent/EP4361527A1/fr
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • 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
    • F25B9/145—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 pulse-tube 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/003—Gas cycle refrigeration machines characterised by construction or composition of the regenerator
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1405—Pulse-tube cycles with travelling waves
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1411—Pulse-tube cycles characterised by control details, e.g. tuning, phase shifting or general control
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1413—Pulse-tube cycles characterised by performance, geometry or theory
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1418—Pulse-tube cycles with valves in gas supply and return lines
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1427—Control of a pulse tube
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures

Definitions

  • the present invention relates to a cryocooler and a method for operating a cryocooler.
  • a multi-system cryocooler including a plurality of cryocoolers
  • the opening and closing timings of the pressure switching valves of the respective cryocoolers coincide with each other when the cryocoolers are operated at the same time the refrigerating performance may deteriorate.
  • an inverter provided in each cryocooler is used to make the operating frequencies of the cryocoolers different and make the valve timing asynchronous (for example, Japanese Unexamined Patent Publication No. 2003-49770 ) .
  • a cryocooler including: a compressor; a plurality of cold heads connected in parallel to the compressor; a pressure sensor that measures a pressure of a working gas on a supply side from the compressor to the plurality of cold heads or on a collection side from the plurality of cold heads to the compressor; and a controller that acquires individual pressure waveform data measured by the pressure sensor when the cold heads are individually operated for each of the plurality of cold heads, and operates the plurality of cold heads at the same time asynchronously based on the individual pressure waveform data.
  • the cryocooler includes a compressor and a plurality of cold heads connected in parallel to the compressor.
  • the method includes measuring a pressure of a working gas on a supply side from the compressor to the plurality of cold heads or on a collection side from the plurality of cold heads to the compressor during individual operation of the cold heads for each of the plurality of cold heads; and operating the plurality of cold heads at the same time asynchronously based on a pressure waveform obtained by measurement.
  • a plurality of cold heads can be operated at the same time asynchronously.
  • Figs. 1 and 2 are views schematically illustrating a cryocooler 10 according to an embodiment.
  • the cryocooler 10 is a two-stage Gifford-McMahon (GM) cryocooler.
  • Fig. 1 illustrates the appearance of the cryocooler 10
  • Fig. 2 illustrates the internal structure of the cryocooler 10.
  • the cryocooler 10 includes a compressor 12 and a plurality of cold heads 14 connected in parallel to the compressor 12.
  • the compressor 12 is configured to collect the working gas of the cryocooler 10 from the cold head 14, pressurize the collected working gas, and supply the working gas to the cold head 14 again.
  • the plurality of cold heads 14 may include at least two cold heads 14, that is, a first cold head 14a and a second cold head 14b.
  • the cold head 14 is also called an expander.
  • the working gas is also referred to as a refrigerant gas and is usually a helium gas, but other suitable gas may be used.
  • the cold head 14 includes a cryocooler cylinder 16, a displacer assembly 18, and a cryocooler housing 20.
  • the cryocooler housing 20 is coupled to the cryocooler cylinder 16, thereby forming a hermetic container that accommodates the displacer assembly 18.
  • the internal volume of the cryocooler housing 20 may be connected to the low pressure side of the compressor 12 and maintained at a low pressure.
  • the cryocooler cylinder 16 has a first cylinder 16a and a second cylinder 16b.
  • the first cylinder 16a and the second cylinder 16b are members having a cylindrical shape, and the second cylinder 16b has a diameter smaller than that of the first cylinder 16a.
  • the first cylinder 16a and the second cylinder 16b are coaxially disposed, and a lower end of the first cylinder 16a is rigidly connected to an upper end of the second cylinder 16b.
  • the displacer assembly 18 has a first displacer 18a and a second displacer 18b.
  • the first displacer 18a and the second displacer 18b are members having a cylindrical shape, and the second displacer 18b has a diameter smaller than that of the first displacer 18a.
  • the first displacer 18a and the second displacer 18b are disposed coaxially with each other.
  • the first displacer 18a is accommodated in the first cylinder 16a, and the second displacer 18b is accommodated in the second cylinder 16b.
  • the first displacer 18a can reciprocate in the axial direction along the first cylinder 16a, and the second displacer 18b can reciprocate in the axial direction along the second cylinder 16b.
  • the first displacer 18a and the second displacer 18b are connected to each other and move integrally.
  • the side close to the top dead center of the axial reciprocation of the displacer is "upper", and the side close to the bottom dead center is “lower”.
  • the top dead center is the position of the displacer where the volume of the expansion space is maximum
  • the bottom dead center is the position of the displacer where the volume of the expansion space is the minimum. Since a temperature gradient is generated in which the temperature drops from the upper side to the lower side in the axial direction during the operation of the cryocooler 10, the upper side can be referred to as a high temperature side and the lower side can be referred to as a low temperature side.
  • the first displacer 18a accommodates a first regenerator 26.
  • the first regenerator 26 is formed by filling a tubular main body portion of the first displacer 18a with a wire mesh such as copper or other appropriate first regenerator material.
  • the upper lid portion and the lower lid portion of the first displacer 18a may be provided as members separate from the main body portion of the first displacer 18a, the upper lid portion and the lower lid portion of the first displacer 18a may be fixed to the main body by appropriate means such as fastening or welding, and accordingly, the first regenerator material may be accommodated in the first displacer 18a.
  • the second displacer 18b accommodates a second regenerator 28.
  • the second regenerator 28 is formed by filling a tubular main body portion of the second displacer 18b with a non-magnetic regenerator material such as bismuth, a magnetic regenerator material such as HoCu 2 , or other appropriate second regenerator material.
  • the second regenerator material may be formed in a granular shape.
  • the upper lid portion and the lower lid portion of the second displacer 18b may be provided as members separate from the main body portion of the second displacer 18b, the upper lid portion and the lower lid portion of the second displacer 18b may be fixed to the main body by appropriate means such as fastening or welding, and accordingly, the second regenerator material may be accommodated in the second displacer 18b.
  • the displacer assembly 18 forms an upper portion chamber 30, a first expansion chamber 32, and a second expansion chamber 34 inside the cryocooler cylinder 16.
  • the cold head 14 includes a first cooling stage 33 and a second cooling stage 35 for heat exchange with a desired object or medium to be cooled by the cryocooler 10.
  • the upper portion chamber 30 is formed between the upper lid portion of the first displacer 18a and the upper portion of the first cylinder 16a.
  • the first expansion chamber 32 is formed between the lower lid portion of the first displacer 18a and the first cooling stage 33.
  • the second expansion chamber 34 is formed between the lower lid portion of the second displacer 18b and the second cooling stage 35.
  • the first cooling stage 33 is fixed to the lower portion of the first cylinder 16a to surround the first expansion chamber 32
  • the second cooling stage 35 is fixed to the lower portion of the second cylinder 16b to surround the second expansion chamber 34.
  • the first regenerator 26 is connected to the upper portion chamber 30 through a working gas flow path 36a formed in the upper lid portion of the first displacer 18a, and is connected to the first expansion chamber 32 through a working gas flow path 36b formed in the lower lid portion of the first displacer 18a.
  • the second regenerator 28 is connected to the first regenerator 26 through a working gas flow path 36c formed from the lower lid portion of the first displacer 18a to the upper lid portion of the second displacer 18b.
  • the second regenerator 28 is connected to the second expansion chamber 34 through a working gas flow path 36d formed in the lower lid portion of the second displacer 18b.
  • the working gas flow between the first expansion chamber 32, the second expansion chamber 34, and the upper portion chamber 30 is not the clearance between the cryocooler cylinder 16 and the displacer assembly 18, but a first seal 38a and a second seal 38b may be provided to be guided to the first regenerator 26 and the second regenerator 28.
  • the first seal 38a may be mounted to the upper lid portion of the first displacer 18a to be disposed between the first displacer 18a and the first cylinder 16a.
  • the second seal 38b may be mounted to the upper lid portion of the second displacer 18b to be disposed between the second displacer 18b and the second cylinder 16b.
  • the cold head 14 includes a pressure switching valve 40 and a driving motor 42.
  • the pressure switching valve 40 is accommodated in the cryocooler housing 20, and the driving motor 42 is attached to the cryocooler housing 20.
  • the pressure switching valve 40 includes the high pressure valve 40a and the low pressure valve 40b, and is configured to generate periodic pressure fluctuation in the cryocooler cylinder 16.
  • the working gas discharge port of the compressor 12 is connected to the upper portion chamber 30 via the high pressure valve 40a, and the working gas suction port of the compressor 12 is connected to the upper portion chamber 30 via the low pressure valve 40b.
  • the high pressure valve 40a and the low pressure valve 40b are configured to selectively and alternately open and close (that is, when one is open, the other is closed).
  • a high pressure (for example, 2 to 3 MPa) working gas is supplied from the compressor 12 to the cold head 14 through the high pressure valve 40a, and a low pressure (for example, 0.5 to 1.5 MPa) working gas is collected from the cold head 14 to the compressor 12 through the low pressure valve 40b.
  • a high pressure (for example, 2 to 3 MPa) working gas is supplied from the compressor 12 to the cold head 14 through the high pressure valve 40a
  • a low pressure for example, 0.5 to 1.5 MPa working gas is collected from the cold head 14 to the compressor 12 through the low pressure valve 40b.
  • the flow direction of the working gas is indicated by an arrow in Fig. 2 .
  • the driving motor 42 is provided to drive the reciprocating motion of the displacer assembly 18.
  • the driving motor 42 is connected to a displacer drive shaft 44 via a motion conversion mechanism 43 such as a Scotch yoke mechanism.
  • the motion conversion mechanism 43 is accommodated in the cryocooler housing 20 similar to the pressure switching valve 40.
  • the displacer drive shaft 44 extends from the motion conversion mechanism 43 into the upper portion chamber 30 through the cryocooler housing 20, and is fixed to the upper lid portion of the first displacer 18a.
  • a third seal 38c is provided in order to prevent leakage of the working gas from the upper portion chamber 30 to the cryocooler housing 20 (which may be maintained at a low pressure as described above).
  • the third seal 38c may be mounted to the cryocooler housing 20 to be disposed between the cryocooler housing 20 and the displacer drive shaft 44.
  • the driving motor 42 When the driving motor 42 is driven, the rotational output of the driving motor 42 is converted into axial reciprocation of the displacer drive shaft 44 by the motion conversion mechanism 43, and the displacer assembly 18 reciprocates in the cryocooler cylinder 16 in the axial direction. Further, the driving motor 42 is connected to the pressure switching valve 40 to selectively and alternately open and close the high pressure valve 40a and the low pressure valve 40b.
  • the cryocooler 10 includes a working gas line 46 that connects the compressor 12 and the plurality of cold heads 14.
  • the working gas line 46 includes a high pressure line 46a for supplying the high pressure working gas from the compressor 12 to the plurality of cold heads 14, and a low pressure line 46b for collecting the low pressure working gas from the plurality of cold heads 14 to the compressor 12.
  • the high pressure line 46a extends from a working gas discharge port of the compressor 12, branches in the middle, and is connected to a pressure switching valve 40 of each cold head 14.
  • the low pressure line 46b extends from a working gas suction port of the compressor 12, branches in the middle, and is connected to a pressure switching valve 40 of each cold head 14. In this manner, as described above, the working gas discharge port of the compressor 12 is connected to the high pressure valve 40a of each cold head 14, and the working gas suction port of the compressor 12 is connected to the low pressure valve 40b of each cold head 14.
  • the cryocooler 10 generates periodic volume fluctuations in the first expansion chamber 32 and the second expansion chamber 34 and pressure fluctuations of the working gas synchronized therewith when the compressor 12 and the driving motor 42 are driven to operate the displacer assembly 18 and the pressure switching valve 40, and accordingly, the refrigeration cycle is configured, and the first cooling stage 33 and the second cooling stage 35 are cooled to a desired cryogenic temperature.
  • the first cooling stage 33 can be cooled to a first cooling temperature in the range of, for example, approximately 20K to approximately 40K.
  • the second cooling stage 35 can be cooled to a second cooling temperature (for example, approximately 1K to approximately 4K) lower than the first cooling temperature.
  • the cryocooler 10 includes a first pressure sensor 48a, a second pressure sensor 48b, and a controller 50.
  • the first pressure sensor 48a measures the pressure of the working gas on the supply side from the compressor 12 to the plurality of cold heads 14, that is, on the high pressure line 46a.
  • the second pressure sensor 48b measures the pressure of the working gas on the collection side from the plurality of cold heads 14 to the compressor 12, that is, on the low pressure line 46b.
  • the first pressure sensor 48a and the second pressure sensor 48b may be collectively referred to as a pressure sensor 48.
  • the pressure sensor 48 is connected to be capable of communicating with the controller 50 by wire or wirelessly, and can transmit the measured pressure waveform data to the controller 50.
  • the first pressure sensor 48a can be installed at any place on the high pressure line 46a.
  • the first pressure sensor 48a may be disposed inside the housing of the compressor 12 and may measure the pressure of the high pressure line 46a inside the compressor 12.
  • the first pressure sensor 48a may be installed in the working gas pipe connecting the compressor 12 and the cold head 14 as the high pressure line 46a.
  • the second pressure sensor 48b can be installed at any place on the low pressure line 46b.
  • the periodic operation of the pressure switching valve 40 may cause a periodic pressure fluctuation (pulsation) in the working gas line 46.
  • a periodic pressure fluctuation pulse
  • the working gas flows from the high pressure line 46a into the cold head 14, and thus the pressure of the high pressure line 46a may decrease to some extent.
  • the high pressure valve 40a is subsequently closed, this pressure drop is restored by supplying a working gas from the compressor 12 to the high pressure line 46a.
  • Such a pressure fluctuation in the high pressure line 46a can be detected by the first pressure sensor 48a. That is, periodic pressure fluctuations may appear in the pressure waveform data measured by the first pressure sensor 48a.
  • a periodic pressure fluctuation that may occur in the low pressure line 46b due to the periodic opening and closing of the low pressure valve 40b may appear.
  • Such a periodic pressure fluctuation reflects the valve timing of the pressure switching valve 40, and thus the phase of the refrigeration cycle of the cold head 14. Therefore, by monitoring the pressure waveform of the working gas line 46 (at least one of the high pressure line 46a and the low pressure line 46b) by using the pressure sensor 48 (at least one of the first pressure sensor 48a and the second pressure sensor 48b), the valve timing of the pressure switching valve 40 can be identified. By acquiring the valve timings of the pressure switching valves 40 for each cold head 14 and starting each cold head 14 such that the valve timings are not synchronized with each other, a plurality of cold heads 14 can be operated at the same time asynchronously.
  • the controller 50 is configured to acquire individual pressure waveform data measured by the pressure sensor 48 when the cold heads 14 are individually operated for each of the plurality of cold heads 14, and operate the plurality of cold heads 14 at the same time asynchronously based on the individual pressure waveform data.
  • the controller 50 is realized as a hardware configuration by elements or circuits such as a central processing unit (CPU) or memory of a computer, and is realized by a computer program or the like as a software configuration.
  • CPU central processing unit
  • memory of a computer and is realized by a computer program or the like as a software configuration.
  • these are drawn as functional blocks realized by their cooperation as appropriate. It is understood by those skilled in the art that the functional blocks can be realized in various forms by combining hardware and software.
  • Fig. 3 is a flowchart illustrating an example of the method for operating the cryocooler 10 according to the embodiment.
  • the processing illustrated in Fig. 3 is executed by the controller 50 in preparation for the normal operation prior to the normal operation of the cryocooler 10 in which the plurality of cold heads 14 are operated at the same time.
  • the controller 50 may operate the plurality of cold heads 14 at the same time asynchronously based on the comparison between the individual pressure waveform data.
  • the first cold head 14a is started (S10).
  • the controller 50 starts the operation of the first cold head 14a by turning on the driving motor 42 of the first cold head 14a.
  • the first cold heads 14a are individually operated. That is, only the first cold head 14a is operated, and the operation of the other cold heads 14 including the second cold head 14b is stopped.
  • the controller 50 acquires individual pressure waveform data measured by the pressure sensor 48 for the first cold head 14a during the individual operation of the first cold head 14a (S11).
  • the individual pressure waveform data is acquired over the refrigeration cycle of at least one or a plurality of cold head 14.
  • the individual pressure waveform data may be the pressure waveform data of the high pressure line 46a measured by the first pressure sensor 48a, or may be the pressure waveform data of the low pressure line 46b measured by the second pressure sensor 48b.
  • the first cold head 14a is stopped (S12).
  • the controller 50 ends the operation of the first cold head 14a by turning on the driving motor 42 of the first cold head 14a.
  • the second cold head 14b is started (S13), individual pressure waveform data is acquired for the second cold head 14b during the individual operation of the second cold head 14b (S14), and then the second cold head 14b is stopped (S15).
  • the controller 50 compares the individual pressure waveform data of the first cold head 14a with the individual pressure waveform data of the second cold head 14b, and determines the phase difference between the two pressure waveforms.
  • the controller 50 determines the generation timing of the pressure fluctuation caused by the same specific valve timing from the individual pressure waveform data of the first cold head 14a and the second cold head 14b, and determines the phase difference between the two pressure waveforms from the time difference thereof.
  • the controller 50 can detect the generation timing of pressure drop of the high pressure line 46a corresponding to the opening timing of the high pressure valve 40a from each of the individual pressure waveform data of the first cold head 14a and the second cold head 14b, and determine the phase difference between the two pressure waveforms from these.
  • the controller 50 operates the plurality of cold heads 14 at the same time asynchronously based on the comparison between the individual pressure waveform data.
  • the controller 50 determines whether or not the phase difference of the determined pressure waveform is non-zero.
  • the controller 50 starts the first cold head 14a and the second cold head 14b at the same time. In this manner, the cold heads are started to operate while the phase difference between the pressure waveforms of the first cold head 14a and the second cold head 14b is kept. Therefore, the valve timings of the two cold heads can be made asynchronous.
  • the controller 50 starts the first cold head 14a and the second cold head 14b with a time difference. That is, one cold head is started first, and the other cold head is started later.
  • the delay time may be a non-integer multiple of one refrigeration cycle of the cold head 14 (that is, one cycle of the pressure waveform). In this manner, the operation of the two cold heads is started with a phase difference corresponding to the delay time. Therefore, the valve timings of the two cold heads can be made asynchronous.
  • the controller 50 can acquire individual pressure waveform data measured by the pressure sensor 48 when the cold heads 14 are individually operated for each of the plurality of cold heads 14, and operate the plurality of cold heads 14 at the same time asynchronously based on the comparison between the individual pressure waveform data.
  • the cryocooler 10 can be provided by operating the plurality of cold heads 14 at the same time asynchronously.
  • the plurality of cold heads 14 can be operated at the same time asynchronously.
  • Fig. 4 is a flowchart illustrating another example of the method for operating the cryocooler 10 according to the embodiment. Similar to the processing of Fig. 3 , the processing illustrated in Fig. 4 is executed by the controller 50 in preparation for the normal operation prior to the normal operation of the cryocooler 10 in which the plurality of cold heads 14 are operated at the same time.
  • the controller 50 acquires total pressure waveform data measured by the pressure sensor 48 when the plurality of cold heads 14 are operated at the same time, acquires a total pressure amplitude from the total pressure waveform data, acquires a total sum of individual pressure amplitudes from the individual pressure waveform data of the plurality of cold heads 14, and operates the plurality of cold heads 14 at the same time asynchronously based on comparison between the total pressure amplitude and the total sum of the individual pressure amplitudes.
  • the first cold head 14a is started (S10), individual pressure waveform data is acquired for the first cold head 14a during the individual operation of the first cold head 14a (S11), and then the first cold head 14a is stopped (S12).
  • the second cold head 14b is started (S13), and individual pressure waveform data is acquired for the second cold head 14b during the individual operation of the second cold head 14b (S14).
  • individual pressure waveform data is acquired for each of the cold heads 14 in the same manner. The acquisition of the individual pressure waveform data can be executed in the same manner as in the processing of Fig. 3 .
  • the plurality of cold heads 14 are operated at the same time (S20).
  • the first cold head 14a is started again after the individual pressure waveform data of the second cold head 14b is acquired.
  • the first cold head 14a and the second cold head 14b are operated at the same time.
  • the stopped cold heads 14 are started again, and all the cold heads 14 are operated at the same time.
  • the controller 50 acquires the total pressure waveform data measured by the pressure sensor 48 during the simultaneous operation of the plurality of cold heads 14 (S21).
  • the total pressure waveform data is acquired over the refrigeration cycle of at least one or a plurality of cold head 14.
  • the total pressure waveform data may be the pressure waveform data of the high pressure line 46a measured by the first pressure sensor 48a, or may be the pressure waveform data of the low pressure line 46b measured by the second pressure sensor 48b.
  • the controller 50 acquires a pressure amplitude from the acquired total pressure waveform data (also referred to as a total pressure amplitude in this specification) (S22). In addition, the controller 50 acquires the pressure amplitude from the individual pressure waveform data of the plurality of cold heads 14 (also referred to as the individual pressure amplitude in this specification), and calculates the total sum of the individual pressure amplitudes (S23).
  • the controller 50 compares the total pressure amplitude and the total sum of the individual pressure amplitudes, and determines the magnitude relationship between the two. It is considered that, when the valve timings of the plurality of cold heads 14 are synchronized, the total pressure amplitude becomes equal to the total sum of the individual pressure amplitudes, and conversely, when the valve timings of the plurality of cold heads 14 are asynchronous, the total pressure amplitude is smaller than the total sum of the individual pressure amplitudes.
  • cryocooler 10 has two cold heads 14
  • the individual pressure amplitudes of the first cold head 14a are represented by A
  • the individual pressure amplitudes of the second cold head 14b are represented by B
  • the controller 50 continues the operation of the plurality of cold heads 14 at the same time (S25).
  • the valve timings of the cold heads of the plurality of cold heads 14 are asynchronous.
  • the controller 50 stops one cold head 14 (for example, the second cold head 14b) once and is started again after a lapse of waiting time (S26).
  • the waiting time may be a non-integer multiple of one refrigeration cycle of the cold head 14 (that is, one cycle of the pressure waveform). In this manner, the operation of the two cold heads is operated with a phase difference corresponding to the waiting time. Therefore, the valve timings of the two cold heads can be made asynchronous.
  • the controller 50 can operate the plurality of cold heads 14 at the same time asynchronously based on the comparison between the total pressure amplitude and the total sum of the individual pressure amplitudes by the same processing.
  • the cryocooler 10 can be provided by operating the plurality of cold heads 14 at the same time asynchronously.
  • the plurality of cold heads 14 can be operated at the same time asynchronously.
  • cryocooler 10 has one compressor 12 is described as an example.
  • the cryocooler 10 may include a plurality of (for example, two) compressors 12.
  • cryocooler 10 is a two-stage GM cryocooler
  • the cryocooler 10 may be a single-stage or multistage GM cryocooler, and may be another type of cryocooler such as a pulse tube cryocooler.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
EP23202568.4A 2022-10-27 2023-10-10 Cryoréfrigérateur et procédé de fonctionnement de cryoréfrigérateur Pending EP4361527A1 (fr)

Applications Claiming Priority (1)

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JP2022172326A JP2024064034A (ja) 2022-10-27 2022-10-27 極低温冷凍機および極低温冷凍機の運転方法

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EP4361527A1 true EP4361527A1 (fr) 2024-05-01

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09130964A (ja) * 1995-10-30 1997-05-16 Sanyo Electric Co Ltd 極低温冷凍装置
US20030024252A1 (en) * 2001-08-03 2003-02-06 Shin Funayama Operation method and operation apparatus for multi-system refrigerators, and refrigerating apparatus
US20190277541A1 (en) * 2017-01-16 2019-09-12 Sumitomo Heavy Industries, Ltd. Cryocooler and control device of cryocooler
US20190316574A1 (en) * 2016-12-02 2019-10-17 Sumitomo Heavy Industries, Ltd. Gm cryocooler and method of operating gm cryocooler
US20220235984A1 (en) * 2019-10-15 2022-07-28 Sumitomo Heavy Industries, Ltd. Cryocooler, and diagnosis device and diagnosis method of cryocooler

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09130964A (ja) * 1995-10-30 1997-05-16 Sanyo Electric Co Ltd 極低温冷凍装置
US20030024252A1 (en) * 2001-08-03 2003-02-06 Shin Funayama Operation method and operation apparatus for multi-system refrigerators, and refrigerating apparatus
JP2003049770A (ja) 2001-08-03 2003-02-21 Sumitomo Heavy Ind Ltd マルチシステム冷凍機の運転方法、装置及び冷凍装置
US20190316574A1 (en) * 2016-12-02 2019-10-17 Sumitomo Heavy Industries, Ltd. Gm cryocooler and method of operating gm cryocooler
US20190277541A1 (en) * 2017-01-16 2019-09-12 Sumitomo Heavy Industries, Ltd. Cryocooler and control device of cryocooler
US20220235984A1 (en) * 2019-10-15 2022-07-28 Sumitomo Heavy Industries, Ltd. Cryocooler, and diagnosis device and diagnosis method of cryocooler

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JP2024064034A (ja) 2024-05-14

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