US20130074523A1 - Cryogenic refrigerator - Google Patents

Cryogenic refrigerator Download PDF

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Publication number
US20130074523A1
US20130074523A1 US13/614,055 US201213614055A US2013074523A1 US 20130074523 A1 US20130074523 A1 US 20130074523A1 US 201213614055 A US201213614055 A US 201213614055A US 2013074523 A1 US2013074523 A1 US 2013074523A1
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United States
Prior art keywords
displacer
refrigerator
cylinder
dead center
valve
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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.)
Abandoned
Application number
US13/614,055
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English (en)
Inventor
Mingyao Xu
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Sumitomo Heavy Industries Ltd
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Sumitomo Heavy Industries Ltd
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Publication date
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Assigned to SUMITOMO HEAVY INDUSTRIES, LTD. reassignment SUMITOMO HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: XU, MINGYAO
Publication of US20130074523A1 publication Critical patent/US20130074523A1/en
Priority to US15/221,726 priority Critical patent/US9829218B2/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
    • 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
    • F25B31/00—Compressor arrangements
    • 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 
    • F25B2309/1406—Pulse-tube cycles with pulse tube in co-axial or concentric geometrical arrangements

Definitions

  • the present invention relates to a cryogenic refrigerator, and more specifically to a cryogenic refrigerator including a displacer.
  • GM refrigerator Gifford McMahon refrigerator
  • This GM refrigerator is known as a cryogenic refrigerator including a displacer.
  • This GM refrigerator is configured to allow the displacer to move back and forth in a cylinder by a drive unit.
  • an expansion space is formed between the cylinder and the displacer.
  • a moving speed of one cycle in which the displacer moves back and forth at one stroke in the cylinder is set to be the same as a speed of a simple harmonic motion.
  • the displacer is in the vicinity of the bottom dead center, and the GM refrigerator performs a process that suctions a high-pressure refrigerator gas into the cylinder.
  • a cryogenic refrigerator including a cylinder, a displacer configured to be moved back and forth in the cylinder by a drive unit, an inlet valve configured to be opened in supplying a refrigerant gas into the cylinder, an exhaust valve configured to be opened in exhausting the refrigerant gas from the cylinder, and an expansion space formed in the cylinder and configured to. generate a cooling by expanding the refrigerant gas caused by back and forth movement of the displacer.
  • a moving speed of the displacer in the vicinity of a bottom dead center is set to be faster than the moving speed of the displacer in the vicinity of a top dead center.
  • FIG. 1 is an outline configuration diagram of a GM refrigerator of a first embodiment of the present invention
  • FIG. 2 is an exploded perspective diagram showing an enlarged Scotch-yoke mechanism provided at the GM refrigerator of the first embodiment of the present invention
  • FIG. 3 is an enlarged diagram showing a slider frame of the Scotch-yoke mechanism
  • FIG. 4 is a motion curve diagram of the displacer in the GM refrigerator of the first embodiment of the present invention.
  • FIGS. 5A through 5H are diagrams for illustrating operation of the Scotch-yoke mechanism provided in the GM refrigerator of the first embodiment of the present invention
  • FIG. 6 is a P-V diagram of the GM refrigerator of the first embodiment of the present invention.
  • FIG. 7 is a diagram showing an effect of the first embodiment of the present invention.
  • FIG. 8 is an enlarged diagram showing a Scotch-yoke mechanism of a modification of the first embodiment
  • FIG. 9 is a motion curve diagram of a displacer in a GM refrigerator of a modification of the first embodiment
  • FIG. 10 is an outline configuration diagram of a GM refrigerator of a second embodiment of the present invention.
  • FIG. 11A is a diagram showing a valve timing of the GM refrigerator of the second embodiment of the present invention.
  • FIG. 11B is a motion curve diagram of a displacer in the GM refrigerator of the second embodiment of the present invention.
  • FIG. 12 is an outline configuration diagram of a GM refrigerator of a modification of the second embodiment.
  • FIG. 13 is an outline configuration diagram of a GM refrigerator of a third embodiment of the present invention.
  • Embodiments of the present invention provide a novel and useful cryogenic refrigerator solving one or more of the problems discussed above.
  • embodiments of the present invention provide a cryogenic refrigerator that can improve a cooling efficiency.
  • FIG. 1 shows a cryogenic refrigerator of a first embodiment of the present invention.
  • the cryogenic refrigerator using a Gifford McMahon cycle (which is hereinafter called “a GM refrigerator”) is taken as an example and described thereof.
  • a GM refrigerator Gifford McMahon cycle
  • application of the present invention is not limited to the GM refrigerator, but is possible for various cryogenic refrigerators using a displacer (e.g., a Solvay refrigerator, a Stirling refrigerator, and the like).
  • the GM refrigerator 1 of the present embodiment is a two-stage refrigerator, which includes a first-stage cylinder 10 and a second-stage cylinder 20 .
  • These first-stage cylinder 10 and second-stage cylinder 20 are formed of a stainless steel with a low thermal conductivity.
  • the high-temperature end of the second-stage cylinder 20 is configured to be coupled to the low-temperature end of the first-stage cylinder 10 .
  • the second-stage cylinder 20 has a diameter smaller than that of the first-stage cylinder 10 .
  • a first-stage displacer 11 and a second-stage displacer 21 are respectively inserted into the first-stage cylinder 10 and the second-stage cylinder 20 .
  • the first-stage displacer 11 and the second-stage displacer 21 are coupled to each other, and are driven to move back and forth in an axial direction of the cylinders 10 , 20 (i.e., arrows Z 1 , Z 2 directions in the drawing) by a drive unit 3 .
  • regenerators 12 , 22 are respectively provided inside the first-stage displacer 11 and the second-stage displacer 21 .
  • the inside of the regenerators 12 , 22 are respectively filled up with regenerator materials 13 , 23 .
  • a space 14 is formed at the high-temperature end in the first-stage cylinder 10
  • a first-stage expansion chamber 15 is formed at the low-temperature end.
  • a second-stage expansion chamber 25 is formed on the low-temperature side of the second-stage cylinder 20 .
  • the first-stage displacer 11 and the second-stage displacer 21 include plural gas passages L 1 through L 4 to let through a refrigerant gas (e.g., helium gas).
  • a refrigerant gas e.g., helium gas
  • the gas passages L 1 connects the space 14 to the regenerator 12
  • the gas passage L 2 connects the regenerator 12 to the first-stage expansion chamber 15
  • the gas passage L 3 connects the first-stage expansion chamber 15 to the regenerator 22
  • the gas passage L 4 connects the regenerator 22 to the second-stage expansion chamber 25 .
  • the space 14 on the high-temperature end side of the fist-stage cylinder is connected to a gas supply system 5 .
  • the gas supply system 5 is configured to include a gas compressor 6 , valves 7 , 8 , a gas passage 9 and the like.
  • An inlet valve 7 is connected to the inlet port side of the gas compressor 6
  • an exhaust valve 8 is connected to the exhaust port side of the compressor 6 .
  • the inlet valve 7 is opened and the exhaust valve 8 is closed, the refrigerant gas is supplied from the gas compressor 6 into the space 14 through the inlet valve 7 and the gas passage 9 .
  • the inlet valve 7 is closed and the exhaust valve 8 is opened, the refrigerant gas in the space 14 is recovered into the gas compressor 6 through the gas passage 9 and the exhaust valve 8 .
  • the drive unit 3 forces the first-stage and second-stage displacers 11 , 21 to move back and forth in the first-stage and second-stage cylinders 10 , 20 .
  • the drive unit 3 is constituted of a motor 30 and a Scotch-yoke mechanism 32 .
  • FIG. 2 shows the enlarged Scotch-yoke mechanism 32 .
  • the Scotch-yoke mechanism 32 is roughly constituted of a crank member 34 and a Scotch-yoke 36 .
  • the crank member 34 is fixed to a rotational shaft (which is hereinafter called “a motor shaft 31 ”).
  • the crank member 34 is configured to include a crank pin 34 a provided at a location eccentric to a mounting position of the motor shaft 31 . Hence, when the crank member 34 is mounted on the motor shaft 31 , the motor shaft 31 and the crank pin 34 a are eccentric to each other.
  • a slide groove 38 is formed so as to extend in directions perpendicular to moving directions of the respective displacers 11 , 21 (i.e., directions shown by arrows X 1 , X 2 ). Accordingly, the Scotch-yoke 36 is formed in a frame shape.
  • the slide groove 38 formed into the Scotch-yoke 36 engages with a roller bearing 35 .
  • the roller bearing 35 is configured to be able to roll in the directions of arrows X 1 , X 2 in the slide groove 38 .
  • a description is given below about a specific configuration of the Scotch-yoke 36 and the slide groove 38 .
  • a crank pin engagement hole 35 a that engages with the crank pin 34 a is formed at the center position of the roller bearing 35 . Accordingly, when the motor shaft 31 is rotated in a state of the crankpin 34 a engaged with the roller bearing 35 , the crank pin 34 a rotates so as to draw an arc, by which the Scotch-yoke 36 moves back and forth in directions of arrows Z 1 , Z 2 . At this time, the roller bearing 35 moves back and forth in the directions of the arrows X 1 , X 2 in the slide groove 38 .
  • the Scotch-yoke 36 is provided with drive arms 37 that extend out in the upward direction and the downward direction.
  • the lower drive arm 37 of the drive arms 37 is coupled to the first-stage displacer 11 as shown in FIG. 1 . Therefore, when the Scotch-yoke 36 moves in the Z 1 , Z 2 directions by the Scotch-yoke mechanism 32 as discussed above, the drive arms 37 moves upward and downward, by which the first-stage and second-stage displacers 11 , 21 are moved back and forth in the first-stage and second-stage cylinders 10 , 20 .
  • a drive of the inlet valve 7 and the exhaust valve 8 is controlled by a rotary valve (not shown in the drawing) driven by the motor 30 .
  • the rotary valve controls the drive so that open and close of the inlet valve 7 and the exhaust valve 8 , and the back and forth motions of the respective displacers 11 , 21 have a predetermined phase difference.
  • This phase difference causes the refrigerant gas to expand in the first-stage expansion chamber 15 and the second-stage expansion chamber 25 , which generates a cooling.
  • the rotary valve opens the exhaust valve 7 of the gas supply system 5 just before the first-stage and second-stage displacers 11 , 21 reach the bottom dead center. More specifically, in the present embodiment, when the first-stage and second-stage displacers 11 , 21 reach a 30 degree point before the bottom dead center (BDC) by the drive unit 3 , the inlet valve 7 is configured to be opened. At this time, the exhaust valve 8 maintains a closed state.
  • the first-stage and second-stage displacers 11 , 21 reach the bottom dead center that minimizes the volume of the first-stage and second-stage expansion chambers 15 , 25 by being driven by the drive unit 3 , and the downward (i.e., the arrow Z 2 direction in the drawing) motion is momentarily stopped (i.e., the moving speed becomes zero).
  • the first-stage and second-stage displacers 11 , 21 start to move upward (i.e., the arrow Z 1 direction in the drawing). This causes the high-pressure refrigerant gas supplied from the gas compressor 6 is supplied into (suctioned into) the first-stage expansion chamber 15 and the second-stage expansion chamber 25 through the above-mentioned route. Then, the inlet valve 7 is closed when the first-stage and second-stage displacers 11 , 21 reach a 121 degree point, and the supply of the refrigerant gas from the gas supply system 5 to the GM refrigerator 1 is stopped.
  • the rotary valve opens the exhaust valve 8 .
  • the inlet valve 7 maintains the closed state. This causes the refrigerant gases in the first-stage and second-stage expansion chambers 15 , 25 to expand, which generates coolings in respective expansion chambers 15 , 25 .
  • the first-stage and second-stage displacers 11 , 21 reach the top dead center by being driven by the drive unit 3 , and stop moving upward (i.e., the arrow Z 1 direction in the drawing), which means the moving speed becomes zero. After that, the first-stage and second-stage displacers 11 , 21 start to move downward (i.e., the arrow Z 2 direction in the drawing).
  • the refrigerant gas expanded in the second-stage expansion chamber 25 flows into the regenerator 22 through the gas passage L 4 ; passes the regenerator 22 , cooling the regenerator material 23 in the regenerator 22 ; and flows into the first-stage expansion chamber through the gas passage L 3 .
  • the refrigerant gas flowed into the first-stage expansion chamber 15 flows into the regenerator 12 through the gas passage L 2 .
  • the refrigerant gas flowed into the regenerator 12 proceeds forward, cooling the regenerator material 13 , and is recovered into the gas compressor 6 of the gas supply system 5 through the gas passage L 1 , the gas passage 9 and the exhaust valve 8 .
  • the exhaust valve 8 is closed when the first-stage and second-stage displacers 11 , 21 reach a 340 degree point, and the recovery (suction) treatment of the refrigerant gas from the GM refrigerator 1 to the gas supply system 5 is stopped.
  • a cryogenic temperature of about 20 to 50 K or less can be generated in the first-stage expansion chamber 15
  • a very low temperature of about 4 to 10 K or less can be generated in the second-stage expansion chamber 25 .
  • FIG. 3 is a diagram of the Scotch yoke 36 as seen from the front.
  • the slide groove 38 that extends in the X 1 , X 2 directions is formed in the Scotch-yoke 36 .
  • a conventional slide groove in the Scotch-yoke is formed into a horizontally long rectangular shape in general.
  • the present embodiment is configured to include a convex part 39 provided at a position corresponding to the bottom dead center (i.e., a position shown by an arrow A in FIG. 3 , which is hereinafter called the “bottom dead center corresponding position A”) of the displacers 11 , 21 in the slide groove 38 so as to protrude upward (i.e., in the Z 1 direction).
  • a concave part 45 is formed about at a position corresponding to the top dead center of the displacers 11 , 21 (i.e., a position shown by an arrow B, which is called hereinafter the “top dead center corresponding position B”) in the slide groove 38 so as to hollow upward (i.e., in the Z 1 direction).
  • a line segment that extends in the vertical direction (i.e., the Z 1 , Z 2 directions) and passes through the bottom dead center corresponding position A is assumed.
  • This line segment is shown by an alternate long and short dashed line in FIG. 3 , and is hereinafter called a center line Z.
  • the above discussed drive arm 37 is configured to form a straight line with the center line Z.
  • the convex part 39 is made of an arc shape centering a position shown by an arrow O in the drawing (which is hereinafter called a center point O), and is configured to form a circular shape part.
  • the convex part 39 has a symmetric shape in an arrow X 1 direction side and an arrow X 2 direction side with the center line Z at its center.
  • angles ⁇ 1 , ⁇ 2 that define a formation range of the convex part 39 are not necessarily set at the same angle to each other as mentioned above, but may be configured to have different angles ( ⁇ 1 ⁇ 2 ).
  • FIG. 4 is a motion curve diagram of the displacers 11 , 21 . Furthermore, FIGS. 5A through 5H show operations of the roller bearing in the slide groove 38 .
  • the transverse axis shows a rotation angle (i.e., crank angle) of the crank member 34
  • the longitudinal axis shows a displacement (travel distance) of the second-stage displacer 21
  • a characteristic of the GM refrigerator 1 of the present embodiment is shown by a solid line (which is shown by an arrow A in the drawing)
  • a characteristic of a conventional GM refrigerator without the convex part 39 and the concave part 45 is shown by an alternate long and short dashed line (which is shown by an arrow B).
  • the crank angle 0 degree is set at a 30 degree point before the bottom dead center (BDC).
  • BDC bottom dead center
  • the roller bearing 35 biases the Scotch-yoke 36 downward (i.e., in a Z 2 direction). This operation causes the roller bearing 35 to be moved in an X 2 direction in a slide groove 38 . More specifically, the roller bearing 35 engages with the convex part 39 caused by the movement, and enters a state of the roller bearing 35 running on the convex part 39 .
  • the crank pin 34 a to which the roller bearing 35 is attached is provided at a position eccentric to the center of the crank member 34 , following the movement of the roller bearing 35 , the Scotch-yoke 36 moves toward the Z 2 direction.
  • the displacers 11 , 21 are connected to the Scotch-yoke 36 via the drive arm 37 . Because of this, as the Scotch-yoke 36 moves, the displacer 11 , 21 move toward the Z 2 direction.
  • the moving speed of the Scotch-yoke 36 (which is equal to the moving speed of the displacers 11 , 21 ) is noted.
  • the convex part 39 protrudes compared to the lower horizontal part 40 .
  • a travel distance of the Scotch-yoke 36 per unit time when the roller bearing 35 is engaged with the convex part 39 is longer than when the roller bearing 35 is engaged with the conventional horizontal part 46 (see FIG. 3 ).
  • the moving speed V 1 of the Scotch-yoke 36 moving downward (in the Z 2 direction) following the movement of the roller bearing 35 (see FIG. 4 ) becomes faster than the moving speed V 1 B of the Scotch-yoke 36 when the roller bearing 35 is engaged with the conventional lower horizontal part 46 (V 1 B ⁇ V 1 ).
  • FIG. 5B shows a state of the crank angle being 30 degrees.
  • the displacers 11 , 21 are set to be the bottom dead center (BDC) when the crank angle is 30 degrees. Due to this, in the bottom dead center, the roller bearing 35 is located at the top (the center position) of the convex part 39 .
  • the crank angle maintains a state of the roller bearing 35 being engaged with the convex part 39 while the crank angle is from the bottom dead center (BDC) to 30 degrees. More specifically, the roller bearing 35 keeps the state of the roller bearing 35 being engaged with the convex part 39 (concretely, a part on the X 2 direction side relative to the center axis Z), and moves to a position facing the horizontal parts 40 , 41 (the state of which is shown in FIG. 5C ).
  • the moving speed V 2 (see FIG. 4 ) of the Scotch-yoke 36 moving upward (in the Z 1 direction) caused by the movement of the roller bearing 35 becomes faster than the moving speed V 2 B of the Scotch-yoke 36 when the roller bearing 35 is engaged with the conventional horizontal part 46 (V 2 B ⁇ V 2 ).
  • V 2 B the moving speed of the Scotch-yoke 36 when the roller bearing 35 is engaged with the conventional horizontal part 46
  • a shape of the convex part 39 is symmetrical about the center line Z in the present embodiment. Accordingly, the moving speeds V 1 , V 2 of the Scotch-yoke 36 in a range of back and forth 30 degrees of the bottom dead center corresponding position A is different in direction but the same in absolute value.
  • the shape of the convex part 39 is made symmetric about the center line Z, production of the Scotch-yoke 36 is made simple.
  • the arc-shaped convex part 39 is structured to directly engage with the horizontal part 40 .
  • a smooth connection part e.g., a straight line
  • a straight line may be provided between the arc-shaped convex part 39 and the horizontal part 40 .
  • FIGS. 5E through 5H show operation of the roller bearing 35 when engaged with the concave part 45 .
  • the concave part 45 is made of a hollow shape relative to the upper horizontal part 41 .
  • a moving speed V 4 of the Scotch-yoke 36 i.e., displacers 11 , 21
  • V 4 B of the Scotch-yoke 36 is slower than a moving speed V 4 B of the Scotch-yoke 36 when the roller bearing 35 is engaged with the conventional horizontal part 47 (V 4 ⁇ V 4 B).
  • the concave part 45 is formed across a range of ⁇ 30 degrees when expressed in a crank angle of the crank member 34 , centering a position to be the top dead center corresponding position B. Accordingly, as shown in FIG. 4 , the moving speed V 4 of the displacers 11 , 21 in the range of ⁇ 30 degrees with the top dead center (TDC) at the center is slower than the moving speed V 4 B of the Scotch-yoke 36 when the roller bearing 35 is engaged with the conventional horizontal part 47 (V 4 ⁇ V 4 B).
  • crank member 34 further rotates from the state shown in FIG. 5G , as shown in FIG. 5H , the roller bearing 35 moves to a position facing the horizontal parts 40 , 41 in the slide groove 38 .
  • This causes the Scotch-yoke 36 to start moving, which further causes the displacers 11 , 21 to start moving.
  • the GM refrigerator 1 of the present embodiment is set so that the moving speeds V 1 , V 2 at the bottom dead center of the displacers 11 , 21 are faster than the moving speed V 4 at the top dead center (V 4 ⁇ V 1 , V 4 ⁇ V 2 ). Therefore, as shown in FIG. 4 , the motion curve of the displacers of the present embodiment (a solid line shown by an arrow A in the drawing) has a steeper characteristic curve than the motion curve of the displacers of the conventional GM refrigerator (an alternate long and short dashed line shown by an arrow B) in the vicinity of the bottom dead center.
  • the moving speeds of the displacers 11 , 21 at the bottom dead center mean moving speeds of the displacers 11 , 21 in a range of the convex part 39 formed in the slide groove 38 .
  • the moving speeds at the top dead center means moving speeds of the displacers 11 , 21 in a range of the concave part 45 formed in the slide groove 38 .
  • the GM refrigerator 1 in the present embodiment is configured to allow the inlet valve 7 to be opened when the displacers 11 , 21 reach the point of 30 degrees before the bottom dead center (BDC) .
  • BDC bottom dead center
  • a timing when the moving speeds of the displacers 11 , 21 (Scotch-yoke 36 ) change in the vicinity of the top dead center is set to be the same as a timing when the inlet valve 7 is opened, but the timing of the inlet valve 7 being opened can be set earlier than the timing when the moving speeds of the displacers 11 , 21 (Scotch-yoke 36 ) change.
  • the moving speeds of the displacers 11 , 21 become approximate the same as the moving speeds of the conventional displacers. More specifically, the moving speeds of the displacers 11 , 21 (Scotch-yoke 36 ) are changed from the moving speed V 2 to the moving speed V 3 at 30 degrees of the crank angle, and become approximately the same as the conventional moving speed V 3 B.
  • the inlet valve 7 in the present embodiment is closed at 121 degrees of the clank angle.
  • the inlet valve 7 As discussed above, by allowing the inlet valve 7 to be opened, the high-pressure refrigerant gas is supplied from the gas supply system to the GM refrigerator 1 .
  • the refrigerant gas has a characteristic whose density increases as pressure increases. Hence, pressure loss becomes small as pressure increases.
  • a gas flow rate from the gas supply system 5 into the GM refrigerator 1 can be increased. In this manner, even if the gas flow rate into the GM refrigerator 1 is increased, the pressure loss is low because the refrigerant gas is at a high pressure.
  • FIG. 6 shows a P-V line diagram of the GM refrigerator 1 in the present embodiment (a characteristic shown by an arrow A), and a P-V line diagram of a GM refrigerator without the convex part 39 in the slide groove 38 (a characteristic shown by an arrow B) as a comparative example together.
  • a cooling capacity generated in one cycle of the GM refrigerator corresponds to an area surrounded by the P-V diagram.
  • the area of the P-V diagram of the present embodiment is larger than that of the P-V diagram of the conventional GM refrigerator. Accordingly, FIG. 6 demonstrates that the GM refrigerator 1 of the present embodiment has a higher cooling efficiency than that of the conventional GM refrigerator.
  • FIG. 7 is a table showing a cooling temperature of the GM refrigerator 1 of the present embodiment, compared with a cooling temperature of the conventional GM refrigerator. In both GM refrigerators, a temperature near the first-stage expansion chamber and a temperature near the second-stage expansion chamber are measured.
  • FIG. 7 also demonstrates that the GM refrigerator 1 of the present embodiment has a higher cooling efficiency than that of the conventional GM refrigerator.
  • FIG. 8 shows a Scotch-yoke mechanism 48 of a GM refrigerator that is a modification of the present embodiment. More specifically, FIG. 8 shows an enlarged Scotch-yoke 49 of the Scotch-yoke mechanism 48 .
  • the same numerals are put to components corresponding to those shown in FIG. 1 through FIG. 5 , and the description is omitted.
  • the Scotch-yoke mechanism 32 provided in the GM refrigerator 1 shown in FIG. 1 through FIG. 5 is configured to provide the concave part 45 in the upper horizontal part 41 of the Scotch-yoke 36 .
  • the present modification features not to provide the concave part 45 in the upper horizontal part 41 but to be configured to be flat.
  • FIG. 9 is a motion curve diagram of displacers 11 , 21 of the GM refrigerator using the Scotch-yoke 49 shown in FIG. 8 .
  • the concave part 45 is not provided in the upper horizontal part 41 , the displacers 11 , 21 are not stopped in the vicinity of the top dead center, and the movement becomes like a simple harmonic motion.
  • moving speed of the displacers 11 , 21 from a point of 30 degrees before the bottom dead center (TDC) to the bottom dead center is V 4 a
  • moving speeds of the displacers 11 , 21 from the top dead center to a point of 30 degrees after the top dead center (TDC) is V 4 b.
  • the configuration of the modification also allows the moving speeds V 1 , V 2 of the displacers 11 , 21 in the vicinity of the bottom dead center to be faster than the moving speeds V 4 a, V 4 b of the displacers 11 , 21 in the vicinity of the top dead center.
  • the cooling efficiency can also be improved like the above-mentioned GM refrigerator 1 of the embodiment.
  • the convex part 39 being an arc shape, but a shape of the convex part 39 is not limited to the arc shape.
  • the convex part 39 has a shape protruding above the lower horizontal part 40 , for example, configuring the convex part 39 by combining plural straight lines and curves is possible.
  • FIG. 10 shows a GM refrigerator 50 of the second embodiment.
  • a description is given about a one-stage GM refrigerator as an example.
  • the GM refrigerator 50 includes a drive unit 51 , a displacer 52 , a cylinder 54 , a cooling stage 55 , a regenerator 57 , compressor 62 and the like.
  • the GM refrigerator of the present embodiment features to adopt a pneumatic mechanism as the drive unit 51 to drive the displacer 52 .
  • the displacer 52 is configured to include a displacer body 52 A, a lower temperature side thermal conduction part 52 B, regenerator 57 and the like.
  • the displacer body 52 A is formed into a cylindrical shape with caps on the end, and the regenerator 57 housing a regenerator material is provided therein.
  • a rectifier 59 that rectifies a flow of a refrigerant gas is provided on the high-temperature side (the upper side is the high-temperature side in the drawing). Furthermore, a rectifier 60 that rectifies a flow of a refrigerant gas is also provided on the low-temperature side (the lower side is the low temperature side in the drawing).
  • a top plate part 52 D that is located at the high-temperature end of the displacer 52 , plural flow passages 61 are provided to flow the refrigerant gas from a room temperature chamber 58 to the regenerator 57 .
  • the room temperature chamber 58 is formed between the top plate part 52 D of the displacer 52 and a top plate part 54 A of the cylinder 54 .
  • This room temperature chamber 58 is connected to the compressor 62 . More specifically, the room temperature chamber 58 is connected to a supply pipe 67 that is connected to a supply side of the compressor 62 , and is connected to a return pipe 68 that is connected to a return side of the compressor 62 .
  • the supply pipe 67 is connected to the room temperature chamber 58 through an inlet valve 63 (which may be called V 1 ).
  • the return pipe 68 is connected to an exhaust valve 64 (which may be called V 2 ) through the room temperature chamber 58 .
  • the respective pipes 67 , 68 join together and become one on the downstream side of the respective valves 63 , 64 and are connected to the room temperature chamber 58 .
  • the inlet valve 63 when the inlet valve 63 is opened and the exhaust valve 64 is closed, the high-pressure refrigerant gas generated by the compressor 62 is supplied to the room temperature chamber 58 .
  • the inlet valve 63 is closed and the exhaust valve 64 is opened, the refrigerant gas is flowed back from the room temperature chamber 58 to the compressor 62 .
  • a low-temperature side thermal conduction part 52 B is provided on the low-temperature end of the displacer 52 . Furthermore, a second passage 66 in communication with the regenerator 57 and an expansion space 53 is formed between the displacer 52 A and the low-temperature side thermal conduction part 52 B. The low-temperature side thermal conduction part 52 B is joined to the displacer body 52 A by using a pin 56 .
  • the expansion space 53 is formed between the cylinder 54 and the displacer 52 (the low-temperature side thermal conduction part 52 B).
  • the high-pressure refrigerant gas from the compressor 62 is introduced into the expansion space 53 .
  • the expansion space 53 is configured to generate a cooling therein by allowing the introduced refrigerant gas to be adiabatically expanded.
  • the cylinder 54 houses the displacer 52 in a movable state therein.
  • the cylinder 54 has a cylindrical shape with caps on the ends, and a cooling stage 55 is provided on the low-temperature end to be an opening side.
  • This cooling stage 55 is thermally connected to an object to be cooled, and the object to be cooled is cooled by a cooling generated in the expansion space 53 .
  • a seal 65 is installed between the cylinder 54 and the displacer 52 . This seal 65 prevents the refrigerant gas supplied from the compressor 62 from passing a gap between the displacer 52 and the cylinder 54 and from flowing into the expansion space 53 .
  • the drive unit 51 On the high-temperature side of the cylinder 54 , a drive unit 51 that drives the displacer 52 is provided.
  • the drive unit 51 is configured to include a drive piston 52 E, a drive chamber 70 , a high-pressure driving valve 71 , a low-pressure driving valve 72 , and the like. Furthermore, in the present embodiment, a high-pressure refrigerant gas generated in the compressor 62 is used as a driving gas.
  • the drive piston 52 E constitutes a wall on the displacer side of the drive chamber 70 , and is configured to be integrated with the displacer 52 .
  • the drive piston 52 E can be provided, for example, so as to protrude upward from the center position of the top plate 52 D of the displacer 52 . Accordingly, when the drive piston 52 E moves up and down, following this, the displacer 52 moves up and down in the cylinder 54 .
  • the drive chamber 70 is formed at the center position of the top place part 54 A of the cylinder 54 .
  • This drive chamber 70 is configured to protrude upward from the top plate 54 A, and the above drive piston 52 E is configured to be movable in a vertical direction (in an axial direction of the cylinder 54 ) in the drive chamber 70 .
  • a seal 73 is installed at a predetermined position of the drive chamber 70 .
  • the seal 73 is installed between an inner wall of the drive chamber 70 and the displacer 52 E. This allows the drive chamber 70 to be configured to be hermetically separated from the room temperature chamber 58 . Moreover, by providing the seal 73 , the drive piston 52 E can move up and down, maintaining a hermetical state of the drive chamber 70 .
  • the drive chamber 70 is connected to the compressor 62 . More specifically, the supply pipe 67 and the return pipe 68 are connected to the drive chamber 70 .
  • the supply pipe 67 is connected to the drive chamber 70 through the high-pressure driving valve 71 (which may be called the valve V 3 ) .
  • the return pipe 68 is connected to the drive chamber 70 through the low-pressure driving valve (which may be called the valve V 4 ).
  • the respective pipes 67 , 68 join together and become one on the downstream side of the drive chamber 70 , and are connected to the drive chamber 70 .
  • the high-pressure driving valve 71 when the high-pressure driving valve 71 is opened and the low-pressure driving valve 72 is closed, the high-pressure refrigerant gas generated in the compressor 62 is supplied to the drive chamber 70 , and a pressure (which is hereinafter called a “P 2 ”) in the drive chamber 70 becomes high.
  • a pressure which is hereinafter called a “P 2 ”
  • the refrigerant gas in the drive chamber 70 flows back to the compressor 62 and the pressure P 2 in the drive chamber 70 becomes low.
  • the pressure P 2 in the drive chamber 70 can be controlled by opening and closing the high-pressure driving valve 71 and the low-pressure driving valve 72 .
  • a pressure (which is hereinafter called a “P 1 ”) in the cylinder 54 can be controlled by open and close of the inlet valve 63 and the exhaust valve 64 .
  • the GM refrigerator 50 of the present embodiment is configured to cause the drive unit 51 to drive the displacer 52 .
  • valves 63 , 64 , 71 and 72 are configured to be integrated as a rotary valve, and the GM refrigerator 50 is configured to cause the displacer 52 to move back and forth once (i.e., to perform one cycle movement) by one revolution of the rotary valve (revolution of 360 degrees).
  • FIGS. 11A and 11B show operation of the GM refrigerator 50 of the present embodiment.
  • FIG. 11A shows valve timing of the GM refrigerator 50 of the present embodiment
  • FIG. 11B shows movement of the displacer 52 in the GM refrigerator 50 .
  • FIG. 11A bold solid lines show periods that respective valves 63 , 64 , 71 and 72 (valves V 1 , V 2 , V 3 and V 4 ) are opened, and a transverse axis shows a rotation angle of the rotary valve (which is hereinafter just called “a valve rotation angle”) .
  • a transverse axis shows a rotation angle of the rotary valve
  • a longitudinal shows an amount of displacement of the displacer 52 .
  • the pressure P 2 in the drive chamber 70 becomes higher than the pressure P 1 in the cylinder 54 (P 1 ⁇ P 2 ). Accordingly, the displacer 52 moves downward toward the bottom dead center (BDC). Here, a moving speed of the displacer 52 in moving downward is made a VC 1 .
  • the bottom dead center (BDC) is set at an earlier angle (lower angle) than the valve rotation angle 90 degrees.
  • the exhaust valve 63 (v 1 ) is set to be opened at an earlier valve rotation angle ⁇ 1 than the bottom dead center (BDC).
  • the high-pressure driving valve 71 (V 3 ) is set to be closed at a valve rotation angle ⁇ 2 between the valve rotation angle ⁇ 1 and the bottom dead center (BDC).
  • the low-pressure driving valve 72 (V 4 ) is opened. Due to this, since the drive chamber 70 is connected to the return pipe 68 , the internal pressure P 2 becomes low. Accordingly, the pressure P 1 in the cylinder 54 becomes higher than the pressure P 2 in the drive chamber 70 , and the displacer 52 moves upward toward the top dead center (TDC). Here, a moving speed of the displacer 52 in moving upward is made a VC 2 .
  • the high-pressure refrigerant gas generated by the compressor 62 is flowed into the expansion space 53 through the room temperature chamber 58 , the flow passage 61 , the regenerator 57 , and the second flow passage 66 .
  • the refrigerant gas is cooled by the regenerator material in the regenerator 57 .
  • the inlet valve 63 (V 1 ) is closed at a valve rotation angle ⁇ 3 .
  • the cylinder 54 is filled up with the high-pressure refrigerant gas, and the internal pressure P 1 is kept high.
  • the low-pressure driving valve 72 (V 4 ) is kept open at the valve rotation angle ⁇ 3 , and the pressure P 2 in the drive chamber 70 is kept low. Because of this, the displacer 52 continues to move upward even at the valve rotation angle ⁇ 3 .
  • the GM refrigerator 50 is configured to open the exhaust valve 64 (V 2 ) at the valve rotation angle 180 degrees.
  • the exhaust valve 64 (V 2 ) is opened, the refrigerant gas in the expansion space 53 expands, and thereby a cooling occurs in the expansion space 53 .
  • the cooling generated in the expansion space 53 cools the object to be cooled connected to the cooling stage 55 .
  • the low-pressure driving valve 72 (V 4 ) is kept opened.
  • the pressure P 2 in the cylinder 54 is low.
  • the low-pressure driving valve 72 (V 4 ) is kept opened.
  • space parts the expansion space 53 , the room temperature chamber 58 and the like formed in the cylinder 54 and the drive chamber 70 are both connected to the return pipe 68 .
  • the low-pressure driving valve 72 (V 4 ) is closed at a valve rotation angle ⁇ 4 . Furthermore, when the low-pressure driving valve 72 (V 4 ) is closed, the high-pressure driving valve 71 (V 3 ) is opened at a valve rotation angle ⁇ 5 after that.
  • the low-pressure driving valve 72 (V 4 ) is closed and the high-pressure driving valve 71 (V 3 ) is opened, by which the high-pressure refrigerant gas is flowed into the drive chamber 70 from the compressor 62 , and the pressure P 2 in the drive chamber 70 is increased.
  • the exhaust valve 64 (V 2 ) is kept opened even at the valve rotation angle ⁇ 5 , and the pressure P 1 in the cylinder 4 is kept low. Accordingly, by allowing the high-pressure driving valve 71 (V 3 ) to be opened, the drive piston 52 E is biased downward, and the displacer 52 start to move downward toward the bottom dead center. A speed of the displacer 52 at this time is made a VC 4 .
  • the moving speeds VC 1 , VC 2 of the displacer 52 in the vicinity of the bottom dead center (BDC) become faster than the moving speed VC 3 in the vicinity of the bottom dead center (TDC) (VC 3 ⁇ VC 1 , VC 3 ⁇ VC 2 ).
  • the low-pressure driving valve 72 (V 4 ) is opened while the valve rotation angle is from the BDC to ⁇ 4 (about 245 degrees) the high-pressure driving valve 71 (V 3 ), compared to the high-pressure driving valve 71 (V 3 ) opened while the valve rotation angle is from ⁇ 5 to ⁇ 2 (about 120 degrees) in one cycle (360 degrees).
  • the moving speeds V 1 , V 2 at the bottom dead center (BDC) of the displacer 52 can be increased as well as the first embodiment, a large amount of refrigerant gas can be supplied into the GM refrigerator 50 (expansion space 53 ) efficiently.
  • the large amount of refrigerant gas can be expanded in the expansion space 53 when a cooling is generated, and the cooling efficiency of the GM refrigerator 50 can be improved.
  • FIG. 12 shows a GM refrigerator 80 of a modification of the GM refrigerator 50 of the second embodiment.
  • FIG. 12 the same numerals are put to components corresponding to those of the GM refrigerator of the second embodiment, and the description is omitted.
  • the GM refrigerator 80 of the present modification features to include a flow passage resistance valve 81 to be a flow resistance provided between the high-pressure driving valve 71 of the supply pipe 67 and the drive chamber 70 .
  • a needle valve that can adjust a valve opening position can be used for this flow passage resistance valve 81 .
  • a differential pressure between the pressure P 1 in the cylinder 54 and the pressure P 2 in the drive chamber 70 can be reduced, and a moving speed of the displacer 52 in the vicinity of the top dead center (TDC) can made be further slower.
  • TDC top dead center
  • a component used for the flow resistance is not limited to the needle valve, but using another component such as an orifice and the like is possible.
  • FIG. 13 shows a GM refrigerator 90 of a third embodiment of the present invention.
  • the GM refrigerator 90 of the present embodiment features a linear motor as a drive unit 91 .
  • This drive unit 91 includes a magnet 92 , a drive inductor 93 , a control unit 94 and the like.
  • the magnet 92 is a bar-shaped magnet in which north poles and south poles are magnetized alternately at a predetermined pitch. This magnet 92 is provided at the center part of the top plate part 52 D of the displacer 52 so as to protrude upward.
  • the drive inductor 93 is constituted of plural electromagnets.
  • the respective electromagnets generate magnetic forces by flowing currents therein.
  • the magnet 92 is inserted into a space formed in the center part of the drive inductor 93 movable in a vertical direction.
  • the drive inductor 93 is connected to the control unit 94 .
  • the control unit 94 is to drive and control the drive inductor 93 . More specifically, the control unit 94 changes a magnitude and a direction of a current supplying to the drive inductor 93 . As discussed above, the magnet 92 is magnetized by the north poles and the south poles alternately at the predetermined pitch. Accordingly, by allowing the control unit 94 to control the magnet poles of the plural electromagnets constituting the drive inductor 93 so as to change subsequently, the magnet 92 moves linearly.
  • the magnet 92 is fixed to the displacer 52 . Hence, by causing the drive inductor 93 to move the magnet 92 , the displacer 52 is also moved. Accordingly, the displacer 52 can be driven by the drive unit 91 .
  • the movement of the displacer 52 by the drive unit 91 can be adjusted by controlling the magnitude and direction of the current flowing through the drive inductor 93 .
  • a micro computer is incorporated in the control unit 94 , and a program that is set to cause the displacer 52 to be moved as shown by the solid lines in FIG. 4 is also incorporated.
  • the displacer 52 is moved as shown by the solid lines in FIG. 4 .
  • the moving speeds V 1 , V 2 at the bottom dead center (BDC) of the displacer 52 can be increased similarly to the first embodiment in the present embodiment, a lot of refrigerant gas can be supplied into the GM refrigerator (cylinders 4 ) efficiently. Accordingly, the lot of refrigerant gas can be expanded in the expansion space 53 in generating a cooling, and the cooling efficiency of the GM refrigerator 90 can be enhanced.
  • a cooling efficiency can be improved because a refrigerant gas can be efficiently supplied into a cylinder in supplying the refrigerant gas.

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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)
US13/614,055 2011-09-28 2012-09-13 Cryogenic refrigerator Abandoned US20130074523A1 (en)

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CN107062673A (zh) * 2017-03-21 2017-08-18 中船重工鹏力（南京）超低温技术有限公司 一种主动气体驱动的gm制冷机
US11221079B2 (en) * 2017-03-13 2022-01-11 Sumitomo Heavy Industries, Ltd. Cryocooler and rotary valve unit for cryocooler
US11333407B2 (en) * 2017-03-10 2022-05-17 Sumitomo Heavy Industries, Ltd. GM cryocooler with buffer volume communicating with drive chamber
US11384963B2 (en) 2016-11-30 2022-07-12 Sumitomo Heavy Industries, Ltd. GM cryocooler

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CN103062949B (zh) * 2011-09-26 2015-05-20 住友重机械工业株式会社 超低温制冷装置
JP2015055374A (ja) 2013-09-10 2015-03-23 住友重機械工業株式会社 極低温冷凍機
JP6573845B2 (ja) * 2016-05-31 2019-09-11 住友重機械工業株式会社 極低温冷凍機
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
JP6781678B2 (ja) * 2016-12-02 2020-11-04 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
JP6842373B2 (ja) * 2017-05-31 2021-03-17 住友重機械工業株式会社 極低温冷凍機
JP6998776B2 (ja) * 2018-01-23 2022-01-18 住友重機械工業株式会社 Ｇｍ冷凍機
JP7164340B2 (ja) 2018-07-11 2022-11-01 住友重機械工業株式会社 極低温冷凍機および極低温冷凍機の流路切替機構
JP2021134951A (ja) * 2020-02-25 2021-09-13 住友重機械工業株式会社 極低温冷凍機および極低温システム

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US11333407B2 (en) * 2017-03-10 2022-05-17 Sumitomo Heavy Industries, Ltd. GM cryocooler with buffer volume communicating with drive chamber
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CN107062673A (zh) * 2017-03-21 2017-08-18 中船重工鹏力（南京）超低温技术有限公司 一种主动气体驱动的gm制冷机

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US20160334144A1 (en) 2016-11-17
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CN103032984A (zh) 2013-04-10
JP5878078B2 (ja) 2016-03-08

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