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WO2018101273A1 - Réfrigérateur gm et procédé de fonctionnement de ce type de réfrigérateur - Google Patents

Réfrigérateur gm et procédé de fonctionnement de ce type de réfrigérateur Download PDF

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Publication number
WO2018101273A1
WO2018101273A1 PCT/JP2017/042659 JP2017042659W WO2018101273A1 WO 2018101273 A1 WO2018101273 A1 WO 2018101273A1 JP 2017042659 W JP2017042659 W JP 2017042659W WO 2018101273 A1 WO2018101273 A1 WO 2018101273A1
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WO
WIPO (PCT)
Prior art keywords
flow path
cylinder
cold head
chamber
refrigerator
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.)
Ceased
Application number
PCT/JP2017/042659
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English (en)
Japanese (ja)
Inventor
名堯 許
乾 包
孝明 森江
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.)
Sumitomo Heavy Industries Ltd
Original Assignee
Sumitomo Heavy Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from JP2017160489A external-priority patent/JP6781678B2/ja
Application filed by Sumitomo Heavy Industries Ltd filed Critical Sumitomo Heavy Industries Ltd
Priority to CN201780071115.1A priority Critical patent/CN109997003B/zh
Publication of WO2018101273A1 publication Critical patent/WO2018101273A1/fr
Priority to US16/427,374 priority patent/US11408406B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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 GM (Gifford-McMahon) refrigerator.
  • GM refrigerators are roughly classified into two types, motor-driven and gas-driven, depending on the drive source.
  • motor drive type the displacer is mechanically connected to the motor and driven by the motor.
  • gas drive type the displacer is driven by gas pressure.
  • the present invention has been made in view of such circumstances, and one of the exemplary purposes of an aspect of the present invention is to provide a multi-cylinder GM refrigerator suitable for practical use.
  • the GM refrigerator includes a first displacer that can reciprocate in the axial direction, a first cylinder that houses the first displacer, and a first drive that drives the first displacer in the axial direction.
  • a first cold head including a piston, a first drive chamber that houses the first drive piston, a second displacer that can reciprocate in an axial direction, a second cylinder that houses the second displacer, and
  • a second cold head comprising: a second drive piston for driving the second displacer in the axial direction; and a second drive chamber for housing the second drive piston; a working gas in the first drive chamber and the second cylinder; Are connected to both the first drive chamber and the second cylinder to supply gas in parallel, and the working gas from the first drive chamber and the second cylinder.
  • the first exhaust valve connected to both the first drive chamber and the second cylinder to collect in parallel, and the first exhaust valve to supply the working gas to the second drive chamber and the first cylinder in parallel.
  • a second intake valve connected to both the two drive chambers and the first cylinder, and the second drive chamber and the first cylinder so as to collect the working gas from the second drive chamber and the first cylinder in parallel.
  • a second exhaust valve connected to both of the two.
  • a GM refrigerator includes a first displacer that can reciprocate in an axial direction, a first drive piston that drives the first displacer in an axial direction, and a first drive piston that houses the first drive piston.
  • a first cold head comprising a first drive chamber; a second displacer capable of reciprocating in the axial direction; and a second cylinder containing the second displacer; and the first drive chamber.
  • a first intake valve connected to both the first drive chamber and the second cylinder so as to supply a working gas to the second cylinder in parallel, and a working gas from the first drive chamber and the second cylinder
  • a first exhaust valve connected to both the first drive chamber and the second cylinder so as to collect them in parallel.
  • a method for operating a gas-driven multi-cylinder GM refrigerator removes the first driving chamber of the first cold head from the first sub-flow path of the GM refrigerator, and removes the first cylinder of the first cold head from the second main flow path of the GM refrigerator. Removing a first cold head from the GM refrigerator, forming a first bypass channel connecting the second main channel to the first sub-channel, and the GM refrigerator While the first cold head is being removed from the GM refrigerator, the working gas is supplied to the second cold head installed in the GM refrigerator, and while the first cold head is being removed from the GM refrigerator And flowing a working gas through the first bypass flow path.
  • a multi-cylinder GM refrigerator suitable for practical use can be provided.
  • FIG. 1 is a schematic view showing a GM refrigerator 10 according to the first embodiment.
  • the GM refrigerator 10 is a multi-cylinder type. Therefore, the GM refrigerator 10 includes a compressor 12 that compresses the working gas (for example, helium gas), and a plurality of cold heads that cool the working gas by adiabatic expansion.
  • the cold head is also called an expander. Since the illustrated GM refrigerator 10 has two cold heads, it can be called a two-cylinder type.
  • the compressor 12 supplies a high-pressure working gas to the cold head.
  • the cold head is provided with a regenerator for precooling the working gas.
  • the precooled working gas is further cooled by expansion in the cold head.
  • the working gas is recovered by the compressor 12 through the regenerator.
  • the working gas cools the regenerator as it passes through the regenerator.
  • the compressor 12 compresses the recovered working gas and supplies it again to the expander.
  • the GM refrigerator 10 includes a first cold head 14a and a second cold head 14b arranged in parallel. These cold heads are single stage. However, the GM refrigerator 10 may include a multistage cold head.
  • the first cold head 14a includes a first displacer 20a that can reciprocate in an axial direction (vertical direction in FIGS. 1 and 2 and indicated by an arrow C), a first cylinder 26a that houses the first displacer 20a, A first drive piston 22a that drives the displacer 20a in the axial direction and a first drive chamber 28a that houses the first drive piston 22a are provided.
  • the second cold head 14b includes a second displacer 20b that can reciprocate in the axial direction, a second cylinder 26b that houses the second displacer 20b, and a second drive piston that drives the second displacer 20b in the axial direction. 22b and a second drive chamber 28b that houses the second drive piston 22b.
  • the GM refrigerator 10 includes a working gas circuit 52 that connects the compressor 12 to the first cold head 14a and the second cold head 14b.
  • the working gas circuit 52 is configured to generate a pressure difference between the first drive chamber 28a and the first cylinder 26a.
  • the working gas circuit 52 is configured to generate a pressure difference between the second drive chamber 28b and the second cylinder 26b.
  • the first displacer 20a and the first drive piston 22a move in the axial direction due to the pressure difference. If the pressure of the first cylinder 26a is low with respect to the first drive chamber 28a, the first drive piston 22a moves downward, and the first displacer 20a also moves downward.
  • the working gas circuit 52 includes a valve portion 54 shared by the first cold head 14a and the second cold head 14b.
  • the valve unit 54 includes a first intake valve V1, a first exhaust valve V2, a second intake valve V3, and a second exhaust valve V4. Although details will be described later, the valve unit 54 is configured to drive the first cold head 14a and the second cold head 14b in the same cycle and in opposite phases.
  • the first intake valve V1 connects the discharge port of the compressor 12 to both the first drive chamber 28a and the second cylinder 26b so as to supply the working gas to the first drive chamber 28a and the second cylinder 26b in parallel.
  • the first exhaust valve V2 connects the suction port of the compressor 12 to both the first drive chamber 28a and the second cylinder 26b so as to collect the working gas from the first drive chamber 28a and the second cylinder 26b in parallel.
  • the second intake valve V3 connects the discharge port of the compressor 12 to both the second drive chamber 28b and the first cylinder 26a so as to supply the working gas to the second drive chamber 28b and the first cylinder 26a in parallel.
  • the second exhaust valve V4 connects the suction port of the compressor 12 to both the second drive chamber 28b and the first cylinder 26a so as to collect the working gas from the second drive chamber 28b and the first cylinder 26a in parallel.
  • FIG. 2 is a schematic diagram showing the first cold head 14 a of the GM refrigerator 10.
  • the second cold head 14b has the same configuration as the first cold head 14a. Therefore, in the following description, the “first cold head 14a”, the “first displacer 20a”, the “first driving piston 22a”, the “first cylinder 26a”, the “first driving chamber 28a”, etc. It can be read as “cold head 14b”, “second displacer 20b”, “second drive piston 22b”, “second cylinder 26b”, “second drive chamber 28b”, and the like.
  • the first cold head 14a is a gas drive type. Therefore, the first cold head 14a includes an axial movable body 16 as a free piston driven by gas pressure, and a cold head housing 18 that is airtight and accommodates the axial movable body 16.
  • the cold head housing 18 supports the axially movable body 16 so as to reciprocate in the axial direction.
  • the first cold head 14a does not have a motor for driving the axially movable body 16 and a coupling mechanism (for example, a Scotch yoke mechanism).
  • the valve portion 54 described above is disposed in the cold head housing 18 of the first cold head 14a (or the second cold head 14b), and may be connected to the compressor 12 and other cold heads by piping.
  • the valve unit 54 is disposed outside the cold head housing 18 and may be connected to the compressor 12, the first cold head 14a, and the second cold head 14b by piping.
  • the axially movable body 16 includes a first displacer 20a and a first drive piston 22a.
  • the first drive piston 22a is disposed coaxially with the first displacer 20a and separated in the axial direction.
  • the cold head housing 18 includes a first cylinder 26a and a first drive chamber 28a.
  • the first drive chamber 28a is disposed coaxially with the first cylinder 26a and adjacent in the axial direction.
  • the drive unit of the first cold head 14a of the gas drive type includes a first drive piston 22a and a first drive chamber 28a. Further, the first cold head 14a includes a gas spring mechanism that acts on the first drive piston 22a so as to reduce or prevent the collision or contact between the first displacer 20a and the first cylinder 26a.
  • the axially movable body 16 includes a connecting rod 24 that rigidly connects the first displacer 20a to the first drive piston 22a so that the first displacer 20a reciprocates in the axial direction integrally with the first drive piston 22a.
  • the connecting rod 24 also extends from the first displacer 20a to the first drive piston 22a coaxially with the first displacer 20a and the first drive piston 22a.
  • the first drive piston 22a has a smaller size than the first displacer 20a.
  • the axial length of the first drive piston 22a is shorter than that of the first displacer 20a, and the diameter of the first drive piston 22a is also smaller than that of the first displacer 20a.
  • the diameter of the connecting rod 24 is smaller than that of the first drive piston 22a.
  • the volume of the first drive chamber 28a is smaller than that of the first cylinder 26a.
  • the axial length of the first drive chamber 28a is shorter than that of the first cylinder 26a, and the diameter of the first drive chamber 28a is also smaller than that of the first cylinder 26a.
  • first drive piston 22a and the first displacer 20a are not limited to that described above, and may be different from that.
  • the dimensional relationship between the first drive chamber 28a and the first cylinder 26a is not limited to that described above, and may be different therefrom.
  • the axial reciprocation of the first displacer 20a is guided by the first cylinder 26a.
  • the first displacer 20a and the first cylinder 26a are each a cylindrical member extending in the axial direction, and the inner diameter of the first cylinder 26a is equal to or slightly larger than the outer diameter of the first displacer 20a.
  • the axial reciprocation of the first drive piston 22a is guided by the first drive chamber 28a.
  • each of the first drive piston 22a and the first drive chamber 28a is a cylindrical member extending in the axial direction, and the inner diameter of the first drive chamber 28a corresponds to the outer diameter of the first drive piston 22a or slightly. Big.
  • the axial stroke of the first drive piston 22a is equal to the axial stroke of the first displacer 20a, and both are integrated over the entire stroke. Move to. The position of the first drive piston 22a relative to the first displacer 20a remains unchanged during the axial reciprocation of the axial movable body 16.
  • the cold head housing 18 includes a connecting rod guide 30 that connects the first cylinder 26a to the first drive chamber 28a.
  • the connecting rod guide 30 extends from the first cylinder 26a to the first drive chamber 28a coaxially with the first cylinder 26a and the first drive chamber 28a.
  • a connecting rod 24 penetrates the connecting rod guide 30.
  • the connecting rod guide 30 is configured as a bearing that guides the axial reciprocation of the connecting rod 24.
  • the first cylinder 26 a is airtightly connected to the first drive chamber 28 a via the connecting rod guide 30.
  • the cold head housing 18 is configured as a working gas pressure vessel.
  • the connecting rod guide 30 may be regarded as a part of either the first cylinder 26a or the first drive chamber 28a.
  • a first seal portion 32 is provided between the connecting rod 24 and the connecting rod guide 30.
  • the first seal portion 32 is attached to either the connecting rod 24 or the connecting rod guide 30 and slides with the other of the connecting rod 24 or the connecting rod guide 30.
  • the first seal portion 32 is configured by a seal member such as a slipper seal or an O-ring, for example.
  • the first drive chamber 28a is configured to be airtight with respect to the first cylinder 26a.
  • the first drive chamber 28a is fluidly isolated from the first cylinder 26a, and no direct gas flow between the first drive chamber 28a and the first cylinder 26a occurs.
  • the first cylinder 26a is divided into an expansion chamber 34 and a room temperature chamber 36 by the first displacer 20a.
  • the first displacer 20a forms an expansion chamber 34 with the first cylinder 26a at one axial end, and forms a room temperature chamber 36 with the first cylinder 26a at the other axial end.
  • the expansion chamber 34 is disposed on the bottom dead center LP side, and the room temperature chamber 36 is disposed on the top dead center UP side.
  • the first cold head 14a is provided with a cooling stage 38 fixed to the first cylinder 26a so as to enclose the expansion chamber 34.
  • the regenerator 15 is built in the first displacer 20a.
  • the first displacer 20 a has an inlet channel 40 that communicates the regenerator 15 with the room temperature chamber 36 at the upper lid. Further, the first displacer 20 a has an outlet channel 42 communicating with the regenerator 15 to the expansion chamber 34 in its cylindrical portion. Or the exit flow path 42 may be provided in the lower cover part of the 1st displacer 20a.
  • the first displacer 20a includes an inlet rectifier 41 inscribed in the upper lid portion and an outlet rectifier 43 inscribed in the lower lid portion. The regenerator 15 is sandwiched between such a pair of rectifiers.
  • a second seal portion 44 is provided between the first displacer 20a and the first cylinder 26a.
  • the second seal portion 44 is, for example, a slipper seal, and is attached to the cylinder portion or the upper lid portion of the first displacer 20a. Since the clearance between the first displacer 20a and the first cylinder 26a is sealed by the second seal portion 44, the direct gas flow between the room temperature chamber 36 and the expansion chamber 34 (that is, the gas flow bypassing the regenerator 15) is Absent.
  • the expansion chamber 34 and the room temperature chamber 36 increase and decrease in a complementary manner. That is, when the first displacer 20a moves downward, the expansion chamber 34 is narrowed and the room temperature chamber 36 is widened. The reverse is also true.
  • the working gas flows from the room temperature chamber 36 into the regenerator 15 through the inlet channel 40. More precisely, the working gas flows from the inlet channel 40 through the inlet rectifier 41 to the regenerator 15. The working gas flows from the regenerator 15 into the expansion chamber 34 via the outlet rectifier 43 and the outlet channel 42. When the working gas returns from the expansion chamber 34 to the room temperature chamber 36, the reverse path is taken. That is, the working gas returns from the expansion chamber 34 to the room temperature chamber 36 through the outlet channel 42, the regenerator 15, and the inlet channel 40. The working gas that bypasses the regenerator 15 and flows through the clearance is blocked by the second seal portion 44.
  • the first drive chamber 28a includes a first section 46a whose pressure is controlled to drive the first drive piston 22a, and a first gas spring chamber 48a partitioned from the first section 46a by the first drive piston 22a.
  • the first drive piston 22a forms a first section 46a with the first drive chamber 28a at one axial end and the first gas spring chamber 48a with the first drive chamber 28a at the other axial end.
  • the first section 46a and the first gas spring chamber 48a increase and decrease in volume complementarily.
  • the first section 46a is disposed on the opposite side in the axial direction from the first cylinder 26a with respect to the first drive piston 22a.
  • the first gas spring chamber 48a is disposed on the same side as the first cylinder 26a in the axial direction with respect to the first drive piston 22a.
  • the upper surface of the first drive piston 22a receives the gas pressure of the first section 46a, and the lower surface of the first drive piston 22a receives the gas pressure of the first gas spring chamber 48a.
  • the second drive chamber 28b includes a second section 46b whose pressure is controlled to drive the second drive piston 22b, and a second gas spring chamber 48b partitioned from the second section 46b by the second drive piston 22b. And comprising.
  • the connecting rod 24 extends from the lower surface of the first drive piston 22a to the connecting rod guide 30 through the first gas spring chamber 48a. Further, the connecting rod 24 extends through the room temperature chamber 36 to the upper lid portion of the first displacer 20a.
  • the first gas spring chamber 48a is disposed on the same side as the connection rod 24 with respect to the first drive piston 22a, and the first section 46a is disposed on the opposite side of the connection rod 24 with respect to the first drive piston 22a.
  • a third seal 50 is provided between the first drive piston 22a and the first drive chamber 28a.
  • the 3rd seal part 50 is a slipper seal, for example, and is attached to the side of the 1st drive piston 22a. Since the clearance between the first drive piston 22a and the first drive chamber 28a is sealed by the third seal portion 50, there is no direct gas flow between the first section 46a and the first gas spring chamber 48a. Further, since the first seal portion 32 is provided, there is no gas flow between the first gas spring chamber 48 a and the room temperature chamber 36. In this way, the first gas spring chamber 48a is formed airtight with respect to the first cylinder 26a. The first gas spring chamber 48 a is sealed by the first seal portion 32 and the third seal portion 50.
  • the first gas spring chamber 48a becomes narrower. At this time, the gas in the first gas spring chamber 48a is compressed and the pressure increases. The pressure in the first gas spring chamber 48a acts upward on the lower surface of the first drive piston 22a. Therefore, the first gas spring chamber 48a generates a gas spring force that resists the downward movement of the first drive piston 22a.
  • first gas spring chamber 48a expands when the first drive piston 22a moves upward.
  • the pressure in the first gas spring chamber 48a decreases, and the gas spring force acting on the first drive piston 22a also decreases.
  • the first section 46a becomes narrow. Therefore, while the second intake valve V3 and the second exhaust valve V4 are closed, another gas spring that generates a downward gas spring force against the upward movement of the first drive piston 22a in the first section 46a. It can also be regarded as a room.
  • the first cold head 14a is installed in the illustrated direction at the site where it is used. That is, the first cold head 14a is installed vertically so that the first cylinder 26a is arranged vertically downward and the first drive chamber 28a is arranged vertically upward.
  • the GM refrigerator 10 has the highest refrigerating capacity when installed in a posture in which the cooling stage 38 is directed downward in the vertical direction.
  • the arrangement of the GM refrigerator 10 is not limited to this.
  • the first cold head 14a may be installed in a posture in which the cooling stage 38 is directed vertically upward.
  • the first cold head 14a may be installed sideways or in other directions.
  • the weight of the axially movable body 16 works to assist the downward driving force of the first driving piston 22a.
  • the first driving piston 22a has a larger driving force when moving downward than when moving upward. Therefore, in a typical gas driven GM refrigerator, the displacer and the displacer cylinder are likely to collide or contact at the bottom dead center of the displacer.
  • the first cold head 14a is provided with a first gas spring chamber 48a.
  • the gas stored in the first gas spring chamber 48a is compressed when the first drive piston 22a moves down, and the pressure increases. Since this pressure acts in the opposite direction to gravity, the driving force acting on the first driving piston 22a is reduced. The speed immediately before the first drive piston 22a reaches the bottom dead center can be reduced.
  • the GM refrigerator 10 may include at least one of the first gas spring chamber 48a and the second gas spring chamber 48b.
  • the valve unit 54 may take the form of a rotary valve. That is, the valve portion 54 may be configured such that the valves V1 to V4 are appropriately switched by the rotational sliding of the valve disk with respect to the valve body.
  • the valve unit 54 may include a rotational drive source 56 for rotationally driving the valve unit 54 (for example, a valve disk).
  • the rotational drive source 56 is a motor, for example.
  • the rotational drive source 56 is not connected to the axially movable body 16 shown in FIG.
  • the valve unit 54 may include a control unit 58 that controls the valve unit 54.
  • the control unit 58 may control the rotational drive source 56.
  • the valve unit 54 may include a plurality of individually controllable valves V1 to V4, and the control unit 58 may control the opening and closing of the valves V1 to V4. In this case, the valve unit 54 may not include the rotational drive source 56.
  • the working gas circuit 52 of the GM refrigerator 10 includes a first intake passage 60, a first exhaust passage 62, a second intake passage 64, a second exhaust passage 66, a first branch passage 68, and a second branch flow.
  • a path 70 is provided.
  • the first intake passage 60 connects the discharge port of the compressor 12 to the first intake valve V1.
  • the first exhaust passage 62 connects the suction port of the compressor 12 to the first exhaust valve V2.
  • the second intake passage 64 connects the discharge port of the compressor 12 to the second intake valve V3.
  • the second exhaust passage 66 connects the suction port of the compressor 12 to the second exhaust valve V4.
  • a part of the second intake passage 64 may be common to the first intake passage 60 on the compressor 12 side.
  • a part of the second exhaust passage 66 may be common to the first exhaust passage 62 on the compressor 12 side.
  • the first branch flow path 68 connects the first drive chamber 28a to both the first intake valve V1 and the first exhaust valve V2, and the second cylinder 26b connects to both the first intake valve V1 and the first exhaust valve V2.
  • the first branch flow path 68 includes a first main flow path 68a connected to the second cylinder 26b, a first sub flow path 68b connected to the first drive chamber 28a, and a first sub flow path 68b. And a first branch point 68c that branches off from the path 68a.
  • the first main flow path 68a is connected to the room temperature chamber 36 of the second cold head 14b, and the first sub flow path 68b is connected to the first section 46a of the first drive chamber 28a.
  • the first branch flow path 68 connects the first intake valve V1 to both the first main flow path 68a and the first sub flow path 68b, and connects the first exhaust valve V2 to the first main flow path 68a and the first sub flow path. 68b is connected to both.
  • the second branch passage 70 connects the second drive chamber 28b to both the second intake valve V3 and the second exhaust valve V4, and connects the first cylinder 26a to both the second intake valve V3 and the second exhaust valve V4.
  • the second branch flow path 70 includes a second main flow path 70a connected to the first cylinder 26a, a second sub flow path 70b connected to the second drive chamber 28b, and a second sub flow path 70b. And a second branch point 70c that branches from the path 70a.
  • the second main flow path 70a is connected to the room temperature chamber 36 of the first cold head 14a, and the second sub flow path 70b is connected to the second section 46b of the second drive chamber 28b.
  • the second branch flow path 70 connects the second intake valve V3 to both the second main flow path 70a and the second sub flow path 70b, and connects the second exhaust valve V4 to the second main flow path 70a and the second sub flow path 70b. 70b is connected to both.
  • FIG. 3 is a diagram illustrating an example of the operation of the GM refrigerator 10.
  • 0 degrees corresponds to the start time of the cycle and 360 degrees corresponds to the end time of the cycle.
  • 90 degrees, 180 degrees, and 270 degrees correspond to 1/4 period, half period, and 3/4 period, respectively.
  • the valve timing illustrated in FIG. 3 is applicable not only to the first embodiment but also to the second to fifth embodiments described later.
  • FIG. 3 illustrates a first intake period A1 and a first exhaust period A2 of the second cold head 14b, and a second intake period A3 and a second exhaust period A4 of the first cold head 14a.
  • the first intake period A1, the first exhaust period A2, the second intake period A3, and the second exhaust period A4 are the first intake valve V1, the first exhaust valve V2, the second intake valve V3, and the second exhaust valve V4, respectively. It is determined by.
  • the working gas is supplied from the discharge port of the compressor 12 to the room temperature chamber 36 of the second cold head 14b through the first main flow path 68a. In parallel, the working gas is also supplied to the first drive chamber 28a through the first sub-channel 68b. Conversely, when the first intake valve V1 is closed, the supply of working gas from the compressor 12 to these two chambers is stopped.
  • the working gas is recovered from the room temperature chamber 36 of the second cold head 14b to the suction port of the compressor 12 through the first main flow path 68a. In parallel, the working gas is also recovered from the first drive chamber 28a through the first sub-channel 68b. When the first exhaust valve V2 is closed, the working gas recovery from these two chambers to the compressor 12 is stopped.
  • the working gas is supplied from the discharge port of the compressor 12 to the room temperature chamber 36 of the first cold head 14a through the second main flow path 70a. In parallel, the working gas is also supplied to the second drive chamber 28b through the second sub-channel 70b. Conversely, when the second intake valve V3 is closed, the supply of working gas from the compressor 12 to both the chambers is stopped.
  • the working gas is recovered from the room temperature chamber 36 of the first cold head 14a to the suction port of the compressor 12 through the second main flow path 70a. In parallel, the working gas is also recovered from the second drive chamber 28b through the second sub-channel 70b. When the second exhaust valve V4 is closed, the recovery of the working gas from these two chambers to the compressor 12 is stopped.
  • the first intake period A1 and the second exhaust period A4 are in the range from the first start timing t1 to the first end timing t2, and the first exhaust period A2 and the second intake period A3 are The range is from the second start timing t3 to the second end timing t4.
  • the first start timing t1 is, for example, 0 degrees.
  • the first end timing t2 is selected from a range of 135 degrees to 180 degrees, for example.
  • the second start timing t3 is, for example, 180 degrees.
  • the second end timing t4 is selected from a range of 315 degrees to 360 degrees, for example.
  • the first intake period A1 is alternately and non-overlapping with the first exhaust period A2, and the second intake period A3 is alternately and non-overlapping with the second exhaust period A4.
  • the first intake period A1 overlaps with the second exhaust period A4, and the first exhaust period A2 overlaps with the second intake period A3.
  • the axial movable body 16 is located at or near the bottom dead center LP at the first start timing t1, and the axial movable body 16 is located at or near the top dead center UP at the second start timing t3.
  • first intake period A1 may not exactly coincide with the second exhaust period A4.
  • the second exhaust period A4 may be at least partially overlapped with the first intake period A1.
  • first exhaust period A2 may not exactly coincide with the second intake period A3.
  • the second intake period A3 may be at least partially overlapped with the first exhaust period A2.
  • the second intake period A3 does not overlap with the first intake period A1.
  • the second exhaust period A4 does not overlap with the first exhaust period A2.
  • the intake / exhaust timing from the compressor 12 to the first cold head 14a is completely deviated from the intake / exhaust timing from the compressor 12 to the second cold head 14b. If it does in this way, the change between the high pressure of the compressor 12 can be suppressed, and the efficiency of the compressor 12 can be improved.
  • the second intake period A3 is preferably delayed from the first intake period A1 by 150 degrees or more.
  • the second exhaust period A4 is preferably delayed from the first exhaust period A2 by 150 degrees or more.
  • the first intake period A1 and the second exhaust period A4 may have different lengths.
  • the first exhaust period A2 and the second intake period A3 may have different lengths.
  • the difference between the intake period and the exhaust period may be, for example, within 20 degrees or within 5 degrees. In this way, the difference in refrigeration capacity between the first cold head 14a and the second cold head 14b may be adjusted.
  • first intake period A1 and the first exhaust period A2 may have different lengths.
  • lengths of the second intake period A3 and the second exhaust period A4 may be different.
  • the difference between the intake period and the exhaust period may be, for example, within 20 degrees or within 5 degrees.
  • FIG. 4 shows the positions of the first displacer 20a and the second displacer 20b at the first start timing t1.
  • FIG. 5 shows the positions of the first displacer 20a and the second displacer 20b at the second start timing t3.
  • FIG. 6 the change of the driving force of the 1st cold head 14a and the 2nd cold head 14b in the driving
  • the upward driving force in the axial direction is represented as positive, and the downward driving force is represented as negative.
  • the first intake period A1 is started (first start timing t1).
  • the first intake valve V1 is opened, and the high-pressure gas is supplied from the discharge port of the compressor 12 to the room temperature chamber 36 of the second cold head 14b.
  • the gas is cooled while passing through the regenerator 15, and enters the expansion chamber 34 of the second cold head 14b.
  • the second exhaust period A4 is started simultaneously with the first intake period A1.
  • the second exhaust valve V4 is opened, and the second section 46b of the second drive chamber 28b is connected to the suction port of the compressor 12. Therefore, the second drive chamber 28 b has a lower pressure than the room temperature chamber 36 and the expansion chamber 34. Therefore, as shown in FIG. 6, an upward driving force acts on the second driving piston 22b in the second cold head 14b.
  • the second displacer 20b As the second drive piston 22b moves upward, the second displacer 20b also moves from the bottom dead center LP toward the top dead center UP.
  • the first intake valve V1 is closed to end the first intake period A1
  • the second exhaust valve V4 is closed to end the second exhaust period A4 (first end timing t2).
  • the second drive piston 22b and the second displacer 20b continue to move toward the top dead center UP.
  • the volume of the expansion chamber 34 of the second cold head 14b is increased and filled with the high pressure gas.
  • the expansion chamber 34 of the first cold head 14a is connected to the suction port of the compressor 12.
  • the first displacer 20a is at a position at or near the top dead center UP of the first cylinder 26a.
  • the high-pressure gas is expanded and cooled in the expansion chamber 34.
  • the expanded gas is recovered by the compressor 12 through the room temperature chamber 36 while cooling the regenerator 15.
  • the first section 46a of the first drive chamber 28a is connected to the discharge port of the compressor 12. Accordingly, the first driving chamber 28a has a higher pressure than the room temperature chamber 36 and the expansion chamber 34, and a downward driving force acts on the first driving piston 22a of the first cold head 14a as shown in FIG.
  • the first drive piston 22a and the first displacer 20a move from the top dead center UP toward the bottom dead center LP, and the low pressure gas is discharged from the expansion chamber 34 of the first cold head 14a.
  • the exhaust process is performed in the first cold head 14a, and the intake process is performed in the second cold head 14b in parallel therewith.
  • the first exhaust period A2 is started (second start timing t3).
  • the first exhaust valve V ⁇ b> 2 is opened, and the expansion chamber 34 of the second cold head 14 b is connected to the suction port of the compressor 12.
  • the high-pressure gas is expanded and cooled in the expansion chamber 34.
  • the expanded gas is recovered by the compressor 12 through the room temperature chamber 36 while cooling the regenerator 15.
  • the second intake period A3 is started simultaneously with the first exhaust period A2.
  • the second intake valve V3 is opened, and the second section 46b of the second drive chamber 28b is connected to the discharge port of the compressor 12. Therefore, the second drive chamber 28 b has a higher pressure than the room temperature chamber 36 and the expansion chamber 34. Therefore, as shown in FIG. 6, a downward driving force acts on the second driving piston 22b in the second cold head 14b.
  • the second displacer 20b also moves from the top dead center UP toward the bottom dead center LP by the downward movement of the second drive piston 22b.
  • the first exhaust valve V2 is closed to end the first exhaust period A2
  • the second intake valve V3 is closed to end the second intake period A3 (second end timing t4).
  • the second drive piston 22b and the second displacer 20b continue to move toward the bottom dead center LP.
  • the volume of the expansion chamber 34 of the second cold head 14b is reduced and the low-pressure gas is discharged.
  • the room temperature chamber 36 of the first cold head 14a is connected to the discharge port of the compressor 12.
  • the first displacer 20a is at a position at or near the bottom dead center LP of the first cylinder 26a.
  • High-pressure gas is supplied from the discharge port of the compressor 12 to the room temperature chamber 36 of the first cold head 14a.
  • the gas is cooled while passing through the regenerator 15, and enters the expansion chamber 34 of the first cold head 14a.
  • the first section 46a of the first drive chamber 28a is connected to the suction port of the compressor 12. Accordingly, the first drive chamber 28a is at a lower pressure than the room temperature chamber 36 and the expansion chamber 34, and an upward driving force acts on the first drive piston 22a of the first cold head 14a as shown in FIG.
  • the first drive piston 22a and the first displacer 20a move from the bottom dead center LP toward the top dead center UP, and the expansion chamber 34 of the first cold head 14a is filled with high-pressure gas.
  • the intake process is performed in the first cold head 14a, and the exhaust process is performed in the second cold head 14b in parallel therewith.
  • the first cold head 14a is driven in the same cycle and opposite phase as the second cold head 14b.
  • the first cold head 14a and the second cold head 14b cool each cooling stage 38 by repeating such a cooling cycle (that is, a GM cycle).
  • a cooling cycle that is, a GM cycle.
  • the GM refrigerator 10 can cool a superconducting device (for example, a superconducting cable) or other object to be cooled (not shown) that is thermally coupled to the cooling stage 38.
  • FIG. 7 is a schematic view showing a GM refrigerator according to a comparative example.
  • a typical gas-driven GM refrigerator has a pair of intake and exhaust valves for intake and exhaust of the expansion chamber, and another set of intake and exhaust valves for intake and exhaust of the drive chamber. Have. That is, four valves of one GM refrigerator are required. Therefore, the two-cylinder GM refrigerator has eight valves V1 to V8 as shown in the figure. The number of valves is large, and the flow path configuration and the drive unit are complicated.
  • the valve unit 54 is shared by the first cold head 14a and the second cold head 14b.
  • FIG. 8 is a schematic view showing the GM refrigerator 10 according to the second embodiment.
  • the GM refrigerator 10 according to the second embodiment is the same as the GM refrigerator 10 according to the first embodiment except that a flow path resistance section such as an orifice is added between the drive chamber and the valve section. is there.
  • the first sub flow path 68b includes a first flow path resistance portion 72a between the first branch point 68c and the first drive chamber 28a.
  • the first flow path resistance portion 72a increases the flow path resistance of the first sub flow path 68b with respect to the first main flow path 68a.
  • the second sub flow path 70b includes a second flow path resistance portion 72b between the second branch point 70c and the second drive chamber 28b.
  • the second flow path resistance portion 72b increases the flow path resistance of the second sub flow path 70b with respect to the second main flow path 70a.
  • the GM refrigerator 10 may include at least one of the first flow path resistance portion 72a and the second flow path resistance portion 72b.
  • FIG. 9 shows a change in driving force of the first cold head 14a in the exhaust process of the first cold head 14a (second exhaust period A4 shown in FIG. 3).
  • the upward driving force in the axial direction is represented as positive, and the downward driving force is represented as negative.
  • FIG. 9 also shows changes in the driving force of the first cold head 14a shown in FIG.
  • the decompression of the first drive chamber 28a is delayed with respect to the decompression of the expansion chamber 34. Thereby, the rising of the downward driving force acting on the first driving piston 22a can be delayed.
  • an upward driving force is applied to the first drive piston 22a from the first start timing t1 to the timing t1 '.
  • the speed immediately before the first drive piston 22a reaches the bottom dead center LP can be reduced. Therefore, contact and collision in the cold head can be suppressed, and vibrations and abnormal noise of the GM refrigerator 10 can be reduced.
  • the drive part of GM refrigerator 10 can be made into a simpler and small structure.
  • At least one of the first flow path resistance portion 72a and the second flow path resistance portion 72b may be provided.
  • FIG. 10 is a schematic view showing a GM refrigerator 10 according to the third embodiment.
  • the GM refrigerator 10 according to the third embodiment is the first except that a third flow path resistance unit 74 such as an orifice communicating the first gas spring chamber 48a and the second gas spring chamber 48b is added. This is the same as the GM refrigerator 10 according to the embodiment.
  • the GM refrigerator 10 includes a short-circuit channel 76 that communicates the first gas spring chamber 48a with the second gas spring chamber 48b.
  • the third flow path resistance unit 74 is disposed in the middle of the short circuit flow path 76.
  • the short-circuit channel 76 is a communication path that directly connects the first gas spring chamber 48a and the second gas spring chamber 48b to each other.
  • the gas stored in the first gas spring chamber 48a is compressed when the first drive piston 22a moves down, and the pressure increases. Contact and collision in the first cold head 14a are suppressed, and vibration and abnormal noise of the GM refrigerator 10 can be reduced.
  • the third flow path resistance portion 74 is provided, when the first drive piston 22a is excessively moved down and the first gas spring chamber 48a is excessively pressurized, the first gas spring chamber 48a is changed to the second flow resistance portion 74. The pressure can be released to the second gas spring chamber 48 b through the three-channel resistance portion 74 and the short-circuit channel 76. Therefore, the first drive chamber 28a is protected.
  • the second gas spring chamber 48b functions in the same manner, and contact and collision with the second cold head 14b are suppressed. In addition, since the pressure can be released from the second gas spring chamber 48b to the first gas spring chamber 48a, the second drive chamber 28b is protected from excessive pressure.
  • the drive part of GM refrigerator 10 can be made into a simpler and small structure.
  • FIG. 11 is a schematic view showing a GM refrigerator 10 according to the fourth embodiment.
  • the GM refrigerator 10 according to the fourth embodiment is the same as the GM refrigerator 10 according to the first embodiment except that the first gas spring chamber 48a and the second gas spring chamber 48b are not provided. That is, the first drive chamber 28a is a single gas chamber, and the first drive piston 22a is a first drive rod that extends from the first displacer 20a to the gas chamber. Similarly, the second drive chamber 28b is a single gas chamber, and the second drive piston 22b is a second drive rod extending from the second displacer 20b to the gas chamber. Even in this case, as in the first embodiment, two cold heads are driven by four valves. Therefore, the drive part of GM refrigerator 10 can be made into a simpler and small structure.
  • FIG. 12 is a schematic view showing a GM refrigerator 10 according to the fifth embodiment.
  • the GM refrigerator 10 according to the fifth embodiment is the same as the GM refrigerator 10 according to the first embodiment except that the second cold head 14b is a motor drive type.
  • the second cold head 14b includes a connection mechanism (for example, a scotch yoke mechanism) 78 that connects the rotational drive source 56 to the second displacer 20b so as to reciprocate the second displacer 20b in the axial direction.
  • the rotational drive source 56 is also coupled to the valve unit 54 so as to rotationally drive the valve unit 54.
  • the first cold head 14a which is a gas drive type as in the above embodiment, is connected to the second intake valve V3 and the second exhaust valve V4 for intake and exhaust of the first cylinder 26a.
  • the room temperature chamber 36 of the first cold head 14a is connected to the second intake valve V3 and the second exhaust valve V4 through the intake / exhaust flow path 80.
  • the first branch flow path 68 connects the first drive chamber 28a to both the first intake valve V1 and the first exhaust valve V2, and the second cylinder 26b connects to both the first intake valve V1 and the first exhaust valve V2. Connect to.
  • FIG. 13 is a schematic view showing a GM refrigerator 10 according to the sixth embodiment.
  • the GM refrigerator 10 according to the sixth embodiment is the same as that of the first embodiment except that the first cold head 14a and the second cold head 14b can be easily detached from the working gas circuit 52, respectively. 10 is the same.
  • the GM refrigerator 10 includes a valve separation mechanism that can separate the first cold head 14a and the second cold head 14b from the valve unit 54 individually.
  • the working gas circuit 52 is provided with a detachable joint 82 such as a self-sealing / coupling.
  • the detachable joint 82 is provided in each of the first sub-channel 68b and the second main channel 70a. Accordingly, the first drive chamber 28a of the first cold head 14a can be removed from the first sub-flow path 68b, and the first cylinder 26a of the first cold head 14a can be removed from the second main flow path 70a. Further, the detachable joint 82 is provided in each of the first main channel 68a and the second sub channel 70b. Therefore, the second drive chamber 28b of the second cold head 14b can be removed from the second sub flow path 70b, and the second cylinder 26b of the second cold head 14b can be removed from the first main flow path 68a.
  • the working gas circuit 52 includes a first bypass channel 84a and a second bypass channel 84b.
  • the first bypass flow path 84a connects the second main flow path 70a to the first sub flow path 68b, and is configured to flow working gas when the first cold head 14a is not installed.
  • the second bypass flow path 84b is configured to connect the first main flow path 68a to the second sub flow path 70b and flow the working gas when the second cold head 14b is not installed.
  • the first bypass channel 84 a and the second bypass channel 84 b are disposed on the valve portion 54 side with respect to the joint 82.
  • the first bypass flow path 84 a includes a fourth flow path resistance portion 86 and an opening / closing valve 88.
  • the fourth flow path resistance portion 86 and the opening / closing valve 88 are connected in series.
  • the fourth flow path resistance portion 86 is provided to give an appropriate flow path resistance to the first bypass flow path 84a.
  • the on-off valve 88 is closed when the first cold head 14a is connected to the working gas circuit 52, and is opened when the first cold head 14a is removed.
  • the on-off valve 88 can be opened and closed manually, for example.
  • the open / close valve 88 may be automatically opened and closed based on the working gas flow rate detected by the flow sensor 90.
  • the flow sensor 90 is provided in the second main flow path 70a so as to detect the working gas flow rate in the second main flow path 70a.
  • the flow sensor 90 may be provided in the first sub flow path 68b so as to detect the working gas flow rate in the first sub flow path 68b.
  • the on-off valve 88 is closed, for example, when the detected working gas flow rate exceeds a certain flow rate threshold value, and is opened when the detected working gas flow rate falls below the flow rate threshold value.
  • the second bypass channel 84b includes a fourth channel resistance portion 86 and an opening / closing valve 88.
  • the on-off valve 88 is closed when the second cold head 14b is connected to the working gas circuit 52, and is opened when the second cold head 14b is removed.
  • the flow sensor 90 may be provided in the first main channel 68a (or the second sub channel 70b).
  • the fourth flow path resistance portion 86 and the opening / closing valve 88 may be replaced by one flow control valve.
  • the working gas flow rate of the first bypass channel 84a (or the second bypass channel 84b) may be adjusted by the flow rate control valve based on the working gas flow rate detected by the flow rate sensor 90.
  • FIG. 14 shows the GM refrigerator 10 according to the sixth embodiment in a state in which the second cold head 14b is installed while the first cold head 14a is detached from the GM refrigerator 10.
  • FIG. 15 is a flowchart illustrating an operation method of the GM refrigerator 10 according to the sixth embodiment.
  • the operator removes the first cold head 14a from the GM refrigerator 10 (S10).
  • the first cold head 14a is removed from the GM refrigerator 10 by removing the first drive chamber 28a from the first sub flow path 68b and removing the first cylinder 26a from the second main flow path 70a.
  • First bypass channel 84a is formed (S12). After removing the first cold head 14a, the operator manually opens the open / close valve 88, thereby forming the first bypass passage 84a. Alternatively, with the removal of the first cold head 14a, the working gas flow rates in the second main flow path 70a and the first sub flow path 68b decrease or become almost zero. This may be detected by the flow sensor 90, the opening / closing valve 88 may be opened, and the first bypass channel 84a may be formed.
  • the working gas is supplied to the second cold head 14b installed in the GM refrigerator 10 (S14).
  • the operation of the second cold head 14b is continued. Thereby, the GM refrigerator 10 can continue cooling the to-be-cooled object.
  • the working gas flows through the first bypass channel 84a (S14).
  • the first bypass passage 84a has a working gas flow rate supplied to the second cold head 14b when the first cold head 14a is not installed.
  • the working gas serves to bypass the second cold head 14b so as not to excessively exceed the supplied standard working gas flow rate.
  • the worker performs maintenance on the removed first cold head 14a (S16). After the maintenance is completed, the operator attaches the first cold head 14a to the GM refrigerator 10 again (S18). Thus, the two cold heads are operated again.
  • the worker can remove the second cold head 14b from the GM refrigerator 10 and perform maintenance.
  • the second bypass channel 84b is formed. While the second cold head 14b is removed from the GM refrigerator 10, the working gas is supplied to the installed first cold head 14a, and the working gas flows through the second bypass passage 84b.
  • the operator can easily remove the cold head from the GM refrigerator 10 during operation of the GM refrigerator 10.
  • the operator can remove one of the other cold heads from the GM refrigerator 10 and perform maintenance while continuing to operate any one of the cold heads.
  • the operator can replace the removed cold head with a new or maintained cold head.
  • the GM refrigerator 10 is provided with a first bypass channel 84a and a second bypass channel 84b. If there is no such bypass flow path, when one cold head is removed, the working gas that should have been supplied to the two cold heads is concentrated on the other cold head in operation. Will be supplied. If it does so, the working gas which flows into the cold head in operation will become excessive, for example, the problem that an excessive high pressure may act on the cold head may arise. However, since the working gas can actually be released through the bypass flow path, the operation of the GM refrigerator 10 can be stably continued as before the cold head is removed.
  • the operation of the GM refrigerator is first stopped, the temperature of the object to be cooled is raised, and then the cold head is maintained. Then, the GM refrigerator must be operated again to recool the object to be cooled. This completes the maintenance. In general, it takes a considerable amount of time to raise and recool the object to be cooled, and as a result, it takes a long time from the start to the completion of maintenance.
  • the GM refrigerator 10 according to the sixth embodiment it is possible to perform maintenance by removing the cold head without increasing the temperature while cooling the object to be cooled of the GM refrigerator 10. Since it is not necessary to raise the temperature of the object to be cooled and to recool it for maintenance, the maintenance can be completed in a short time.
  • FIG. 16 shows an alternative embodiment for the bypass flow path.
  • the GM refrigerator 10 is not provided with the first bypass flow path 84a and the second bypass flow path 84b.
  • an alternative bypass tube 92 is attached to the working gas circuit 52 when the first cold head 14a is removed.
  • the bypass pipe 92 forms a first bypass flow path that connects the second main flow path 70a to the first sub flow path 68b.
  • the bypass pipe 92 may include a fourth flow path resistance portion 86 when necessary.
  • the bypass pipe 92 is removed, and the first cold head 14a is attached instead. Even if it does in this way, the effect that the excessive supply of the working gas to the 2nd cold head 14b can be suppressed like the 1st bypass channel 84a shown in Drawing 13 and Drawing 14 can be produced.
  • bypass pipe 92 is attached instead, and a second bypass flow path connecting the first main flow path 68a to the second sub flow path 70b can be formed.
  • the above-described bypass configuration can be similarly applied to the two-cylinder GM refrigerator 10 having the eight valves V1 to V8 illustrated in FIG. 7, and thereby the same effect can be achieved.
  • the first cold head 14 a and the second cold head 14 b can be individually detached by a joint 82.
  • a first bypass passage 84a is provided between the first cold head 14a and the first valve group (V3, V4, V7, V8), and the second cold head 14b and the second valve group (V1, V2, V5, V5). V6) is provided with a second bypass channel 84b.
  • an alternative bypass pipe 92 may be attached.
  • one compressor 12 is provided with one valve unit 54, and two cold heads are driven.
  • two valve units 54 may be connected to one compressor 12 in parallel.
  • a four-cylinder GM refrigerator having one compressor 12 and four cold heads can be configured.
  • a GM refrigerator having one compressor 12 and an even number of cold heads can be configured.
  • the present invention can be used in the field of GM refrigerators.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un réfrigérateur GM (10) comprenant : une première tête froide (14a) qui comprend un premier élément de déplacement (20a) qui peut effectuer un mouvement de va-et-vient dans la direction axiale, un premier piston d'entraînement (22a) qui entraîne le premier élément de déplacement (20a) dans la direction axiale, et une première chambre d'entraînement qui loge le premier piston d'entraînement; une seconde tête froide (14b) qui comprend un second élément de déplacement (20b) qui peut effectuer un mouvement de va-et-vient dans la direction axiale et un second cylindre (26b) qui loge le second élément de déplacement (20b); une première soupape d'admission V1 qui est reliée à la fois à la première chambre d'entraînement (28a) et au second cylindre (26b) de façon à fournir de manière parallèle un gaz de travail à la première chambre d'entraînement (28a) et au second cylindre (26b); et une première soupape d'échappement V2 qui est reliée à la fois à la première chambre d'entraînement (28a) et au second cylindre (26b) de façon à collecter de manière parallèle le gaz de travail provenant de la première chambre d'entraînement (28a) et du second cylindre (26b).
PCT/JP2017/042659 2016-12-02 2017-11-28 Réfrigérateur gm et procédé de fonctionnement de ce type de réfrigérateur Ceased WO2018101273A1 (fr)

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CN201780071115.1A CN109997003B (zh) 2016-12-02 2017-11-28 Gm制冷机及gm制冷机的运转方法
US16/427,374 US11408406B2 (en) 2016-12-02 2019-05-31 GM cryocooler and method of operating GM cryocooler

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JP2016234924 2016-12-02
JP2017-160489 2017-08-23
JP2017160489A JP6781678B2 (ja) 2016-12-02 2017-08-23 Ｇｍ冷凍機およびｇｍ冷凍機の運転方法

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WO2020012869A1 (fr) * 2018-07-11 2020-01-16 住友重機械工業株式会社 Congélateur à température ultra-basse, et mécanisme de commutation de trajet d'écoulement d'un congélateur à température ultra-basse
CN110953110A (zh) * 2019-12-16 2020-04-03 边令仁 一种整流式液涡轮机及其工作方法

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JPH0547761U (ja) * 1991-03-27 1993-06-25 三菱重工業株式会社 ガスサイクル冷凍機
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WO2020012869A1 (fr) * 2018-07-11 2020-01-16 住友重機械工業株式会社 Congélateur à température ultra-basse, et mécanisme de commutation de trajet d'écoulement d'un congélateur à température ultra-basse
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CN110953110A (zh) * 2019-12-16 2020-04-03 边令仁 一种整流式液涡轮机及其工作方法
WO2021120592A1 (fr) * 2019-12-16 2021-06-24 边令仁 Turbine à liquide du type à conditionnement et son procédé de fonctionnement

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