US20130219923A1 - Cryogenic refrigerator - Google Patents

Cryogenic refrigerator Download PDF

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Publication number
US20130219923A1
US20130219923A1 US13/775,424 US201313775424A US2013219923A1 US 20130219923 A1 US20130219923 A1 US 20130219923A1 US 201313775424 A US201313775424 A US 201313775424A US 2013219923 A1 US2013219923 A1 US 2013219923A1
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Prior art keywords
cylinder
displacer
cryogenic refrigerator
time
pressure
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Abandoned
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US13/775,424
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English (en)
Inventor
Yoji Mizuno
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Sumitomo Heavy Industries Ltd
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Sumitomo Heavy Industries Ltd
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Assigned to SUMITOMO HEAVY INDUSTRIES, LTD. reassignment SUMITOMO HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Mizuno, Yoji
Publication of US20130219923A1 publication Critical patent/US20130219923A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • 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

Definitions

  • the present invention relates to a cryogenic refrigerator that produces cryogenic temperatures by causing the Simon expansion using a high-pressure refrigerant gas fed from a compressor.
  • cryogenic refrigerators have been used for a wider variety of purposes, there is a demand for increases in their outputs.
  • Conventionally, as a common practice for improving the performance of the cryogenic refrigerator it has been performed to increase the diameter of a cylinder, the stroke length of a displacer, and the high-low pressure difference of a refrigerant gas of the cryogenic refrigerator.
  • a cryogenic refrigerator includes a first cylinder and a second cylinder; a first displacer and a second displacer configured to reciprocate inside the first cylinder and the second cylinder, respectively; an intake and outlet system configured to alternately perform a first operation of supplying gas to the first cylinder and discharging the gas from the second cylinder and a second operation of discharging the gas from the first cylinder and supplying the gas to the second cylinder; a communication path configured to communicate the first cylinder with the second cylinder; and an opening and closing part configured to open and close the communication path.
  • FIG. 1 is a schematic diagram illustrating a cryogenic refrigerator according to an embodiment of the present invention
  • FIG. 2 is a schematic diagram illustrating a connection mechanism of the cryogenic refrigerator according to the embodiment
  • FIG. 3 is a diagram illustrating a configuration of a first displacer and a second displacer according to the embodiment
  • FIG. 4 is a schematic diagram illustrating a Scotch yoke mechanism of the cryogenic refrigerator according to the embodiment
  • FIG. 5 is a timing chart illustrating valve timing of valves of the cryogenic refrigerator according to this embodiment
  • FIG. 6 is a timing chart illustrating the valve timing of the cryogenic refrigerator along with the positions of the first and second displacers, the pressures inside first and second cylinders, and pressures on the high-pressure side and the low-pressure side of a compressor according to the embodiment;
  • FIG. 7 is a schematic diagram illustrating a variation of the embodiment.
  • the compressor unit including multiple compressors increases in size and decreases in efficiency, and an increase in operational loads on the compressor unit is likely to reduce the useful service life of the compressor unit. That is, the conventional art has yet to provide a cryogenic refrigerator that makes it possible to achieve higher output more efficiently.
  • a cryogenic refrigerator is provided that makes it possible to achieve higher output more efficiently.
  • the opening operation of an opening and closing part allows a high-pressure refrigerant gas taken in into one of a first cylinder and a second cylinder from a compressor to be provided to the other one of the first cylinder and the second cylinder.
  • a high-pressure refrigerant gas is allowed to be provided from the other one to the one of the first cylinder and the second cylinder. This reduces variations on both the high-pressure side and the low-pressure side of the compressor, so that it is possible to reduce operational loads on the compressor.
  • FIG. 1 and FIG. 2 are diagrams for illustrating a cryogenic refrigerator 1 according to an embodiment of the present invention.
  • FIG. 1 is a diagram illustrating a piping structure of the cryogenic refrigerator 1 .
  • FIG. 2 is a diagram illustrating a drive structure of the cryogenic refrigerator 1 .
  • the cryogenic refrigerator 1 of this embodiment is a Gifford-McMahon (GM) refrigerator that uses helium gas as a refrigerant gas.
  • GM Gifford-McMahon
  • the cryogenic refrigerator 1 includes a first cylinder 2 , a first displacer 3 , a second cylinder 4 , a second displacer 5 , an intake and outlet system 6 including a group of pipes and a group of valves V 1 , V 2 , V 3 , and V 4 , a connecting pipe 7 (a communication path), and a communicating valve V 5 (an opening and closing part).
  • the cryogenic refrigerator 1 further includes a microcomputer (not graphically illustrated) as a control part that controls the opening and closing of the valves V 1 through V 4 and the communicating valve V 5 .
  • the group of pipes of the intake and outlet system 6 includes a first supply pipe 61 , a first outlet pipe 62 , a second supply pipe 63 , a second outlet pipe 64 , a first supply and outlet common pipe 65 , and a second supply and outlet common pipe 66 .
  • the first supply pipe 61 has a first end connected to a high-pressure side H of a compressor 8 .
  • the first supply pipe 61 has a second end connected to the first supply and outlet common pipe 65 that is connected to the first cylinder 2 .
  • the first intake valve V 1 is provided in a middle portion of the first supply and outlet common pipe 65 .
  • the second supply pipe 63 has a first end connected to a middle portion of the first supply pipe 61 .
  • the second supply pipe 63 has a second end connected to the second supply and outlet common pipe 66 connected to the second cylinder 4 .
  • the second intake valve V 3 is provided in a middle portion of the second supply and outlet common pipe 66 .
  • the second outlet pipe 64 has a first end connected to a low-pressure side L of the compressor 8 .
  • the second outlet pipe 64 has a second end connected to the second supply and outlet common pipe 66 connected to the second cylinder 4 .
  • the second outlet valve V 4 is provided in a middle portion of the second supply and outlet common pipe 66 .
  • the first outlet pipe 62 has a first end connected to a middle portion of the second outlet pipe 64 .
  • the first outlet pipe 62 has a second end connected to the first supply and outlet common pipe 65 connected to the first cylinder 2 .
  • the first outlet valve V 2 is provided in a middle portion of the first supply and outlet common pipe 65 .
  • the first cylinder 2 and the second cylinder 4 include a common flange part 90 .
  • the upper end of the first cylinder 2 and the upper end of the second cylinder 4 are open at the upper surface of the flange part 90 .
  • the upper end of the first cylinder 2 and the upper end of the second cylinder 4 are hermetically closed by a common lid part 9 .
  • FIG. 3 a description is given, with reference to FIG. 3 , of a configuration of the first displacer 3 and the second displacer 5 of this embodiment.
  • the first displacer 3 and the second displacer 5 have the same configuration. Therefore, in FIG. 3 , a description is given using the first displacer 3 and a description of the second displacer 5 is omitted. Further, when necessary, the reference numerals of components of the second displacer 5 are shown in parentheses.
  • the first cylinder 2 accommodates the first displacer 3 in such a manner as to allow the first displacer 3 to reciprocate in the longitudinal directions of the first cylinder 2 (the directions of arrows Z 1 and Z 2 in FIG. 3 ).
  • the second cylinder 4 accommodates the second displacer 5 in such a manner as to allow the second displacer 5 to reciprocate in the longitudinal directions of the second cylinder 4 (the directions of arrows Z 1 and Z 2 in FIG. 3 ).
  • stainless steel is used for the first cylinder 2 and the second cylinder 4 in terms of ensuring strength, thermal conductivity, helium blocking capability, etc.
  • Each of the first displacer 3 and the second displacer 5 has a cylindrical shape, and has a channel space formed inside where a refrigerant gas flows.
  • the channel space is filled with a regenerator material to form a regenerator 117 .
  • a room temperature chamber 108 A is formed between the first cylinder 2 and the high temperature end of the first displacer 3 .
  • a room temperature chamber 108 B is formed between the second cylinder 4 and the high temperature end of the second displacer 5 .
  • An opening 116 through which helium gas is introduced into or let out of the first expansion space 113 A or the second expansion space 113 B is formed at the low temperature end of each of the first displacer 3 and the second displacer 5 .
  • the first expansion space 113 A and the second expansion space 113 B change in volume with the reciprocations of the first displacer 3 and the second displacer 5 , respectively.
  • a seal member 115 is attached between part of the first displacer 3 near its high temperature end and the first cylinder 2 and between part of the second displacer 5 near its high temperature end and the second cylinder 4 .
  • the regenerator material is formed of, for example, a wire mesh.
  • the cryogenic refrigerator 1 includes a drive mechanism that drives the first displacer 3 and the second displacer 5 in different phases.
  • the drive mechanism includes a Scotch yoke mechanism 70 and a connection mechanism 80 .
  • FIG. 4 is a schematic diagram illustrating the Scotch yoke mechanism 70 .
  • the Scotch yoke mechanism 70 includes a crank member 77 and a Scotch yoke 78 .
  • the crank member 77 is connected to an output shaft (motor shaft) 74 of a motor (a drive part).
  • the crank member 77 includes a crank pin 75 that is eccentric to the output shaft 74 and extends parallel to the output shaft 74 .
  • the Scotch yoke 78 includes a horizontally elongated frame part 32 in which a window part 34 is formed, a drive shaft 31 , and a cylindrical crank pin bearing 11 .
  • the frame part 32 is formed in a middle portion of the drive shaft 31 . That is, the frame part 32 forms part of the drive shaft 31 .
  • the lower end of the drive shaft 31 is fixed to an upper part of the first displacer 3 .
  • the crank pin bearing 11 is rollably provided in the window part 34 .
  • the crank pin 75 is slidably received by the inner wall surface of the crank pin bearing 11 .
  • the drive shaft 31 projects upward and outward from the upper part of the first displacer 3 through an insertion hole 9 a of the lid part 9 .
  • a driven shaft 51 is fixed to an upper part of the second displacer 5 .
  • the driven shaft 51 projects upward and outward from the upper part of the second displacer 5 through an insertion hole 9 b of the lid part 9 .
  • the first arm part 12 has a first end part 12 a, a second end part 12 b, and a center part 12 c rotatably connected to an upper end part of the drive shaft 31 , an upper end part of the driven shaft 51 , and an upper part of the support member 21 , respectively, by connecting members 16 such as pins.
  • the second arm part 13 has a first end part 13 a, a second end part 13 b, and a center part 13 c rotatably connected to part of the drive shaft 31 below the frame part 32 , a middle part of the driven shaft 51 , and a middle part of the support member 21 , respectively, by connecting members 17 such as pins.
  • first arm part 12 and the second arm part 13 have their respective center parts 12 c and 13 c connected to the support member 21 , being vertically spaced apart from each other, so as to be oscillatable in directions indicated by arrows A 1 and A 2 in FIG. 2 about the points of connection.
  • crank pin 75 is rotated by the motor, so that the crank pin bearing 11 causes the drive shaft 31 and the first displacer 3 to vertically reciprocate while sliding (rolling) in the longitudinal directions of the window part 34 .
  • valve timing VT which is indicated by a bold line in FIG. 5 , is schematically illustrated with blocks in (e) of FIG. 6 .
  • the first displacer 3 and the second displacer 5 are driven to be opposite in phase.
  • Pressure P illustrated in (b) of FIG. 6 the pressure inside the expansion space 113 A of the first cylinder 2 is indicated by a solid line, and the pressure inside the expansion space 113 B of the second cylinder 4 is indicated by a broken line.
  • Time t 1 of FIG. 5 and FIG. 6 is slightly before the time at which the position DP of the second displacer 5 is at the bottom dead center D.
  • the communicating valve V 5 is opened by the control part, and continues to be open for a predetermined period of time so as to allow high-pressure helium gas inside the second cylinder 4 to be supplied into the first cylinder 2 via the connecting pipe 7 .
  • This predetermined period of time is determined based on the time taken for the pressure P inside the second cylinder 4 to lower from high pressure H to low pressure L (lowering time) or the time taken for the pressure P inside the first cylinder 2 to rise from low pressure L to high pressure H (rising time) illustrated in (b) of FIG. 6 .
  • This lowering time or rising time may be determined by, for example, an experiment or a simulation, and in general, the predetermined period of time is determined to be approximately the half of the lowering time or rising time. That is, at time t 2 , when the predetermined period of time has passed, the pressure P inside the second cylinder 4 and the pressure P inside the first cylinder 2 are substantially equal.
  • the communicating valve V 5 is closed by the control part. Further, at time t 2 , the first intake valve V 1 is opened to allow high-pressure helium gas to be supplied from the high-pressure side H of the compressor 8 into the first cylinder 2 via the first supply pipe 61 and the first supply and outlet common pipe 65 , so that the pressure P inside the first cylinder 2 is caused to be high H. Further, at time t 3 , when a predetermined period of time has passed since time t 2 , the first intake valve V 1 is closed.
  • Time t 4 in FIG. 5 and FIG. 6 is slightly before the time at which the position DP of the first displacer 3 is at the bottom dead center D.
  • the communicating valve V 5 is opened by the control part, and continues to be open for a predetermined period of time so as to allow high-pressure helium gas inside the first cylinder 2 to be supplied into the second cylinder 4 via the connecting pipe 7 .
  • the pressure P inside the second cylinder 4 and the pressure P inside the first cylinder 2 are substantially equal.
  • the communicating valve V 5 is closed by the control part. Further, at time t 5 , the second intake valve V 3 is opened to allow high-pressure helium gas to be supplied from the high-pressure side H of the compressor 8 into the second cylinder 4 via the second supply pipe 63 and the second supply and outlet common pipe 66 , so that the pressure P inside the second cylinder 4 is caused to be high H. Further, at time t 6 , when a predetermined period of time has passed since time t 5 , the second intake valve V 3 is closed.
  • the first outlet valve V 2 is opened to allow helium gas inside the first cylinder 2 to be discharged to the low-pressure side L of the compressor 8 via the first supply and outlet common pipe 65 and the first outlet pipe 62 , so that the pressure P inside the first cylinder 2 is caused to be low L.
  • the first outlet valve V 2 is closed.
  • High-pressure helium gas inside the second cylinder 4 flows into the first cylinder 2 via the communicating valve V 5 and the connecting pipe 7 , so that the pressure inside the second cylinder 4 decreases and the pressure inside the first cylinder 2 increases.
  • the communicating valve V 5 is opened, the communicating valve V 5 is closed, the first intake valve V 1 is opened, and the second outlet valve V 4 is opened by the control part.
  • High-pressure helium gas flows from the high-pressure side H of the compressor 8 into the first cylinder 2 via the first supply pipe 61 and the first supply and outlet common pipe 65 .
  • High-pressure helium gas inside the second cylinder 4 flows into the low-pressure side L of the compressor 8 via the second supply and outlet common pipe 66 and the second outlet pipe 64 .
  • the first expansion space 113 A is filled with the high-pressure helium gas, and the first intake valve V 1 is closed as described above.
  • the first displacer 3 is positioned at the bottom dead center D inside the first cylinder 2 .
  • the first outlet valve V 2 is opened slightly before this time, the helium gas of the first expansion space 113 A adiabatically expands.
  • the helium gas of the first expansion space 113 A whose temperature has been lowered by the adiabatic expansion absorbs the heat of the cooling stage 10 .
  • the first displacer 3 moves toward the top dead center U, so that the volume of the first expansion space 113 A decreases.
  • the helium gas inside the first expansion space 113 A is returned to the intake side, that is, the low-pressure side L, of the compressor 8 via the opening 116 , the regenerator 117 , and the opening 111 .
  • the regenerator material is cooled by the helium gas. This process is employed as one cycle, and the cryogenic refrigerator 1 cools the cooling stage 10 by repeating this cooling cycle.
  • the cryogenic refrigerator 1 of this embodiment using the first displacer 3 and the corresponding first cylinder 2 and the second displacer 5 and the corresponding second cylinder 4 as a pair, it is possible to cause the paired first and second cylinders 2 and 4 to supply a high-pressure refrigerant gas to each other without the intervention of the compressor 8 based on suitable opening and closing of the communicating valve V 5 by causing the first displacer 3 and cylinder 2 and the second displacer 5 and cylinder 4 to operate in antiphase to each other.
  • valve timing VT( 4 V) in a four-valve GM refrigerator that is not provided with the communicating valve V 5 and the connecting pipe 7 of this embodiment is illustrated in (c).
  • the first intake valve V 1 is open and the second outlet valve V 4 is open between time t 1 and time t 3
  • the second intake valve V 3 is open and the first outlet valve V 2 is open between time t 4 and time t 6 .
  • the waveform of pressure variations on the high-pressure side and the waveform of pressure variations on the low-pressure side of a compressor in this case of the four-valve GM refrigerator are illustrated as PV( 4 V) in (d) of FIG. 6 .
  • the waveform of pressure variations on the high-pressure side H and the waveform of pressure variations on the low-pressure side L of the compressor 8 in the five-valve cryogenic refrigerator 1 of this embodiment are illustrated as PV in (f) of FIG. 6 .
  • cryogenic refrigerator 1 of this embodiment it is possible to reduce operational loads on the compressor 8 . Accordingly, a compressor unit including the compressor 8 is prevented from increasing in size or degrading in efficiency. Further, according to this embodiment, it is possible to reduce pressure variations, so that it is possible to control reduction in the useful service life of the compressor unit due to an increase in its operational loads. In addition, it is possible to reduce the workload of the compressor 8 , so that it is possible to save energy.
  • the configuration is illustrated where the first through fourth valves V 1 through V 4 and the communicating valve V 5 included in the intake and outlet system 6 are independent solenoid valves, while these valves V 1 through V 5 may be replaced with a valve plate and an valve body that form a known rotary valve.
  • the rotary valve may be configured by connecting the valve plate to the output shaft 74 of the motor (drive part) that drives the Scotch yoke mechanism 70 positioned above the lid part 9 of the first cylinder 2 and the second cylinder 4 illustrated in FIG. 2 , and suitably fixing the valve body above the lid part 9 . That is, the control part may be omitted in the case of using a rotary valve.
  • the number of stages is one in the cryogenic refrigerator 1
  • this number of stages may be suitably selected from two, three, etc.
  • the number of pairs of displacers is not limited to one, and may be two or more.
  • cryogenic refrigerator is a GM refrigerator.
  • present invention is not limited to this, and embodiments of the present invention may also be applied to any refrigerators having a displacer, such as Stirling refrigerators and Solvay cycle refrigerators.
  • the definitions of the top dead center and the bottom dead center may be opposite to the above-described definitions.
  • the above-illustrated method of determining a predetermined period of time or a fixed time is a mere example, and a predetermined period of time or a fixed time may be defined as another proportion based on the lowering time or rising time.
  • a compressor unit including the compressor is prevented from increasing in size or degrading in efficiency.
  • embodiments of the present invention may be applied to various kinds of cryogenic refrigerators.

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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)
US13/775,424 2012-02-27 2013-02-25 Cryogenic refrigerator Abandoned US20130219923A1 (en)

Applications Claiming Priority (2)

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JP2012040635A JP2013174411A (ja) 2012-02-27 2012-02-27 極低温冷凍機
JP2012-040635 2012-02-27

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170115036A1 (en) * 2015-10-23 2017-04-27 Sumitomo Heavy Industries, Ltd. Gm cryocooler
US11371754B2 (en) * 2016-06-02 2022-06-28 Sumitomo Heavy Industries, Ltd. GM cryocooler
US11408406B2 (en) 2016-12-02 2022-08-09 Sumitomo Heavy Industries, Ltd. GM cryocooler and method of operating GM cryocooler
US12516852B2 (en) * 2021-04-30 2026-01-06 Sumitomo Heavy Industries, Ltd. Cryocooler and method for operating cryocooler

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Publication number Priority date Publication date Assignee Title
JP2016118367A (ja) * 2014-12-24 2016-06-30 住友重機械工業株式会社 極低温冷凍機
JP6664843B2 (ja) * 2015-10-23 2020-03-13 住友重機械工業株式会社 Ｇｍ冷凍機
WO2018101273A1 (ja) * 2016-12-02 2018-06-07 住友重機械工業株式会社 Ｇｍ冷凍機およびｇｍ冷凍機の運転方法
JP6781651B2 (ja) * 2017-03-13 2020-11-04 住友重機械工業株式会社 極低温冷凍機、極低温冷凍機用のロータリーバルブユニット及びロータリーバルブ
CN107843022B (zh) * 2017-10-25 2024-07-26 中国电子科技集团公司第十六研究所 一种双驱动旋转分置式斯特林制冷机
CN114585867B (zh) * 2019-10-15 2023-08-15 住友重机械工业株式会社 超低温制冷机、超低温制冷机的诊断装置及诊断方法

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170115036A1 (en) * 2015-10-23 2017-04-27 Sumitomo Heavy Industries, Ltd. Gm cryocooler
US10184693B2 (en) * 2015-10-23 2019-01-22 Sumitomo Heavy Industries, Ltd. GM cryocooler
US11371754B2 (en) * 2016-06-02 2022-06-28 Sumitomo Heavy Industries, Ltd. GM cryocooler
US11408406B2 (en) 2016-12-02 2022-08-09 Sumitomo Heavy Industries, Ltd. GM cryocooler and method of operating GM cryocooler
US12516852B2 (en) * 2021-04-30 2026-01-06 Sumitomo Heavy Industries, Ltd. Cryocooler and method for operating cryocooler

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JP2013174411A (ja) 2013-09-05

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