US20140020407A1 - Regenerative refrigerator - Google Patents

Regenerative refrigerator Download PDF

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Publication number: US20140020407A1
Authority: US; United States
Prior art keywords: stage; regenerative; regenerator; refrigerant gas; magnetic
Prior art date: 2012-07-20
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

US13/871,100

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English (en)

Inventor

Mingyao Xu

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.)

2012-07-20

Filing date

2013-04-26

Publication date

2014-01-23

2013-04-26 Application filed by Sumitomo Heavy Industries Ltd filed Critical Sumitomo Heavy Industries Ltd

2013-04-26 Assigned to SUMITOMO HEAVY INDUSTRIES, LTD. reassignment SUMITOMO HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: XU, MINGYAO

2014-01-23 Publication of US20140020407A1 publication Critical patent/US20140020407A1/en

2017-08-09 Priority to US15/672,449 priority Critical patent/US10203135B2/en

Status 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/003—Gas cycle refrigeration machines characterised by construction or composition of the regenerator

Definitions

the present invention generally relates to a regenerative refrigerator.
a Gifford-McMahon (GM) refrigerator, a pulse tube refrigerator, or the like is known as a regenerative refrigerator for cooling an object by an adiabatic expansion of a refrigerant gas and accumulating cooling generated by the adiabatic expansion of the refrigerant gas.
These regenerative refrigerators include a regenerator for accumulating cooling generated when the refrigerant gas is adiabatically expanded.
a regenerative material is filled in the regenerator in order to accumulate cooling as disclosed in Japanese Laid-open Patent Publication No. 2008-224161. For example, lead is used as the regenerative material.
One aspect of the embodiments of the present invention may be to provide a regenerative refrigerator including a regenerator filled with a regenerative material for accumulating cooling of a refrigerant gas, wherein the regenerator is divided into a central region and a peripheral region on a cross-sectional face of the regenerator, and a specific heat of the central region is larger than a specific heat of the peripheral region.
FIG. 1 schematically illustrates the inside of a regenerative refrigerator of a first embodiment
FIG. 2 is a cross-sectional view taken along a line A-A of FIG. 1 ;
FIGS. 3A and 3B illustrate flow rate distribution of a refrigerant gas inside a second stage displacer
FIG. 4 schematically illustrates the inside of a regenerative refrigerator of a second embodiment
FIG. 5 schematically illustrates the inside of a regenerative refrigerator of a third embodiment
FIG. 6 schematically illustrates the inside of a regenerative refrigerator of a fourth embodiment
FIGS. 7A , 7 B, and 7 C are plan views for explaining a filler provided in a regenerative refrigerator of a fourth embodiment.
a magnetic regenerative material such as HoCu 2 or the like having a specific heat larger than that of lead in the temperature range of 30K or less.
a magnetic regenerative material shows phase transition in a temperature range of 15K or less so as to change to an anti-ferromagnetic material. Because the magnetic regenerative material has a magnetic susceptibility larger than lead or the like, high-efficiency regenerative effect is possible.
the magnetic regenerative material is mainly made of a rare-earth material. Therefore, it is difficult to obtain the magnetic regenerative material and the cost of the magnetic regenerative material is high.
One object of the embodiments is to provide a regenerative refrigerator which can provide a high-efficiency regenerative effect at a low cost.
a specific heat in a central region where the flow rate of a refrigerant gas is high is increased to be larger than the specific heat in a peripheral region where the flow rate of a refrigerant gas is low. Therefore, the regenerator efficiency can be enhanced.
FIG. 1 is a cross-sectional view of a regenerative refrigerator of a first embodiment.
a two-stage Gifford-McMahon (GM) refrigerator using a helium gas as a refrigerant gas is exemplified as a regenerative refrigerator 1 A.
the first embodiments are applied to not only the GM refrigerator but also various refrigerators (for example, a pulse tube refrigerator or the like) which have a regenerator filled with a regenerative material.
the regenerative refrigerator 1 A includes a first stage displacer 2 , a second stage displacer 20 , a first stage cylinder 4 , a second stage cylinder 30 , a first stage cooling stage 5 , a second stage cooling stage 27 , a first stage regenerator 17 , a second stage regenerator 26 , a compressor 12 , and so on.
the first stage displacer 2 has a cylindrical shape.
the first stage displacer 2 includes a first stage displacer main body 2 A, a first stage heat exchanging portion 2 B, a first stage regenerator 17 , and so on.
the first stage displacer main body 2 A is shaped like a cylinder having a bottom.
a regenerative material 7 is filled in the first stage displacer main body 2 A.
the first stage regenerator 17 which is filled with the regenerative material 7 , is provided.
the regenerative material 7 may be made of lead, copper, or the like having a large specific heat (a volumetric specific heat) in a temperature range of 15K or higher.
a flow smoother 9 is provided on the high temperature side of the first stage regenerator 17 in order to control a flow of a refrigerant gas.
the upper side corresponds to the high temperature side.
a flow smoother 10 is provided on the low temperature side of the first stage regenerator 17 in order to control the flow of the refrigerant gas.
the lower side corresponds to the lower temperature side.
a first flow path 11 is formed to allow a refrigerant gas to flow from the room temperature chamber 8 to the first stage regenerator 17 , which is formed on the high temperature side of the first stage displacer 2 .
the room temperature chamber 8 is a space formed between the upper surface of the first stage cylinder 4 and the upper surface of the first stage displacer 2 .
a supply and discharge system (described later) is connected to the room temperature chamber 8 .
a first stage heat exchanging portion 2 B is provided on a low temperature end of the first stage displacer 2 .
a second flow path 16 is formed between the first stage displacer main body 2 A and the first stage heat exchanging portion 2 B to connect the first stage regenerator 17 to a first stage expansion space 3 .
the first stage heat exchanging portion 2 B is connected to the first stage displacer 2 using a pin 6 .
the first stage expansion space 3 is a space formed between the lower surface of the first stage cylinder 4 and the lower surface of the first stage heat exchanging portion 2 B (first stage displacer 2 ).
a high pressure refrigerant gas is introduced into the first stage expansion space 3 via the second flow path 16 .
a first stage cooling stage 5 is provided at a position corresponding to the first stage expansion space 3 of the first stage cylinder 4 .
the above first stage displacer 2 is installed in the first stage cylinder 4 .
a driving mechanism such as a scotch yoke mechanism is connected to the high temperature end of the first stage displacer 2 .
the first stage displacer 2 reciprocates in the first stage cylinder 4 by the scotch yoke mechanism.
a seal 15 is installed at a predetermined position between the first stage displacer 2 and a top flange.
the seal 15 hermetically divides the first stage expansion space 3 from a room temperature chamber 8 .
the second stage cylinder 30 is integrally formed on a low temperature end portion of the first stage cylinder 4 .
the second stage cylinder 30 accommodates the second stage displacer 20 so that the second stage displacer 20 is movable in the second stage cylinder 30 .
the second stage displacer 20 is in a cylindrical shape and is connected to the low temperature end portion of the first stage displacer 2 .
a pin 19 a is installed in the low temperature end of the first stage heat exchanging portion 2 B.
a pin 19 b is installed in the high temperature end of the second stage displacer 20 .
the pins 19 a and 19 b are connected by a connector 19 c.
the second stage displacer 20 is connected to the first stage displacer 2 .
the second stage displacer 20 also reciprocates in the second stage cylinder 30 along with the reciprocation of the first stage displacer 2 .
the second stage displacer 20 includes a second stage displacer main body 20 A, a second stage heat exchanging portion 20 B, a second stage regenerator 26 , and so on.
a second stage displacer main body 20 A is in a cylindrical shape having a bottom, and has a second stage regenerator 26 in the second stage displacer main body 20 A.
the above second stage displacer 2 is installed in the second stage cylinder 30 .
a third flow path 24 is formed to allow the refrigerant gas to flow from a first stage expansion space 3 to the second stage regenerator 26 formed on the high temperature side of the second stage displacer 20 .
the second stage heat exchanging portion 20 B is installed on a low temperature end of the second stage displacer 2 .
a fourth flow path 29 is formed between the second stage displacer main body 20 A and the second stage heat exchanging portion 20 B to connect the second stage regenerator 26 to a second stage expansion space 28 .
the second stage expansion space 28 is a space formed between the lower surface of the second stage cylinder 30 and the lower surface of the second stage heat exchanging portion 20 B (second stage displacer 20 ).
a high pressure refrigerant gas is introduced into the second stage expansion space 28 via the fourth flow path 29 .
a second stage cooling stage 27 is provided at a position corresponding to the second stage expansion space 28 of the second stage cylinder 30 .
the supply and discharge system includes a compressor 12 , a supply valve 13 , a return valve 14 , and so on.
a high pressure refrigerant gas which is generated by the compressor 12 , is supplied into a room temperature chamber 8 .
a low pressure refrigerant gas flows back into the compressor 12 .
the refrigerant gas from the compressor 12 flows into the first stage regenerator 17 via the room temperature chamber 8 and the first flow path 11 .
the high pressure refrigerant gas which is cooled by exchanging heat with the regenerative material 7 in the first stage regenerator 17 , is supplied into the first stage expansion space 3 via the second flow path 16 .
the refrigerant gas supplied to the first stage expansion space 3 flows into the second stage regenerator 26 via the third flow path 24 .
the refrigerant gas exchanges heat with regenerative materials 40 and 42 (described below) so as to be cooled and is supplied to the second stage expansion space 28 via the fourth flow path 29 .
the first and second stage displacers 2 , 20 are moved toward the upper dead end by the scotch yoke mechanism. With this, the volumes of the first and second stage expansion spaces 3 and 28 are increased. At this time, the refrigerant gas continues to be supplied to the first and second stage expansion spaces 3 and 28 via the first and second regenerators 17 and 26 .
the expanded refrigerant gas flows back to a low pressure side of the compressor 12 via the first and second stage regenerators 17 and 26 and the flow paths 11 , 16 , 24 , and 29 .
the regenerative materials 7 , 40 , and 42 in the first and second regenerators 17 and 26 accumulate cooling of the refrigerant gas.
the first stage expansion space 3 is cooled to be, for example, about 40K and the second stage expansion space is cooled to be, for example, about 4K.
FIG. 2 is a cross-sectional view of the second stage displacer 20 illustrated in FIG. 1 taken along a line A-A.
FIG. 3 illustrates a flow distribution of the refrigerant gas flowing through the second stage displacer 20 .
the second stage regenerator 26 has a separating member 31 on the high temperature side and a separating member 32 on the low temperature side.
the regenerative materials 40 and 42 fill a space formed by the separating members 31 and 32 .
the separating members 31 and 32 prevent the regenerative materials 40 and 42 from flowing therethrough, the refrigerant gas can freely pass through the separating members 31 and 32 .
a cross-sectional face of the second stage regenerator 26 is divided into a central region 21 , which is shaped substantially like a circle and positioned in the vicinity of the center, and a peripheral region 22 , which is shaped like a ring and positioned around the central region 21 .
a flow rate of the refrigerant gas in the second stage regenerator 26 is described.
the refrigerant gas flows through the inside of the second stage displacer 20 .
the supply valve 13 is opened, the refrigerant gas flows through the high temperature end to the low temperature end inside the second stage displacer 20 (in the downward direction in FIGS. 1 and 3B ).
the return valve 14 is opened, the refrigerant gas flows through the low temperature end to the high temperature end inside the second stage displacer 20 (in the upward direction in FIGS. 1 and 3A ).
FIG. 3A illustrates a flow distribution of the refrigerant gas inside the second stage displacer 20 from the low temperature end to the high temperature end.
FIG. 3B illustrates a flow distribution of the refrigerant gas inside the second stage displacer 20 from the high temperature end to the low temperature end.
the lengths of arrows in FIGS. 3A and 3B correspond to the flow rates of the refrigerant gas flowing in the second stage regenerator 26 .
the flow distribution of the refrigerant gas flowing through the second stage displacer 20 is not even in a flowing direction of the refrigerant gas.
the flow rate (hereinafter, a “central region flow rate”) of the refrigerant gas is larger in the central region 21 of second stage displacer 20 .
the flow rate (hereinafter, a “peripheral region flow rate”) of the refrigerant gas on the peripheral region 22 is less than that of the central region 21 of the second stage displacer 20 . This is because the flow path resistance of the refrigerant gas on the central region 21 is less than the flow path resistance of the refrigerant gas on the peripheral region 22 .
the second stage displacer 20 in association with the flow distribution of the refrigerant gas inside the second stage regenerator 26 , the second stage displacer 20 is divided into the central region 21 and the peripheral region 22 on the cross-sectional face. Specifically, by dividing the separating member 33 (corresponding to a separating member recited in claims) in the above cylindrical shape, which is provided in a boundary between the central region 21 and the peripheral region 22 , to thereby divide the central region 21 and the peripheral region 22 .
the separating member 33 is provided in an upper portion of the separating member 32 , which is provided on the low temperature end side inside the second stage regenerator 26 .
the separating member 33 allows the refrigerant gas to pass through in a manner similar to other separating members 31 and 32 . However, the separating member 33 prevents the regenerative material from passing through.
two types of the nonmagnetic regenerative material 40 and the magnetic regenerative material 42 are used as the regenerative material filling the second stage regenerator 26 .
bismuth or an alloy containing bismuth is used as the nonmagnetic regenerative material 40 .
HoCu 2 is used as the magnetic regenerative material 42 .
the magnetic regenerative material 42 such as HoCu 2 has a specific heat (a volumetric specific heat) larger than the nonmagnetic regenerative material 40 such as bismuth under an ultralow temperature of 30K or less.
the second stage displacer 20 has an ultralow temperature of 15K or less when the regenerative refrigerator 1 A operates. Therefore, when the regenerative refrigerator 1 A operates, the second stage regenerator 26 has a temperature of 30K or less.
the magnetic regenerative material 42 has specific heat larger than the specific heat of the nonmagnetic regenerative material 40 .
the magnetic material 42 having a larger specific heat is provided in the central region 21 .
the magnetic material 40 having a less specific heat than that of the magnetic regenerative material 42 is provided in the peripheral region 22 . Therefore, the specific heat of the central region 21 becomes larger than the specific heat of the peripheral region 22 .
the magnetic regenerative material 42 having a large specific heat is provided in the central region where the flow rate of the refrigerant gas is large, it is possible to enhance an efficiency of accumulating cooling of the second stage regenerator 26 .
the filling amount (the amount to use) of the magnetic regenerative material 42 can be reduced in comparison with the structure in which the magnetic regenerative material 42 is provided in the entire second stage regenerator.
the magnetic regenerative material 42 is provided in the central region 21 in the vicinity of the low temperature end.
the peak of the volume specific heat is as low as 5K to 10K. Therefore, an efficiency of accumulating cooling is high by providing HoCu 2 on the low temperature end in the central region 21 .
the height of the separating member 33 separating the nonmagnetic regenerative material 40 from the magnetic regenerative material 42 is set to be less than the overall height of the second stage regenerator 26 .
the magnetic regenerative material 42 is provided only in the vicinity of the low temperature end.
the separating member 34 is provided in the upper portion of the magnetic regenerative material 42 , which fills the inside of the separating member 33 , so that the nonmagnetic regenerative material 40 is not mixed with the magnetic regenerative material 42 .
bismuth is used as the nonmagnetic regenerative material 40
HoCu 2 or the like is used as the magnetic regenerative material 42 .
the materials of the nonmagnetic regenerative material 40 and the magnetic regenerative material 42 are not limited to these. Other materials may be used.
the magnetic regenerative material 42 is preferably made of a material having a peak of the specific heat at 30K or less.
the nonmagnetic regenerative material 40 is preferably made of lead instead of bismuth or the like. However, in consideration of the environment, it is preferable to use bismuth or the like.
a ratio between cross-sectional areas of the central and peripheral regions is appropriately selected depending on the capability and the size of the refrigerator. It is preferable that the central region occupies from about 50% to about 95%.
the regenerative materials 40 and 42 fill the inside of the second stage regenerator 26 , it is preferable to fill the regenerative materials 40 and 42 so that the pressure loss of the refrigerant gas flowing through the central region becomes greater than the pressure loss of the refrigerant gas flowing through the peripheral region.
FIGS. 4 to 7C regenerative refrigerators 1 B to 1 D of second to fourth embodiments are described.
the same reference symbols are attached to the structures corresponding to the structures illustrated in FIGS. 1 to 3B and description of these portions is omitted.
FIG. 4 schematically illustrates a regenerative refrigerator 1 B of the second embodiment.
only one type of the magnetic regenerative material 42 is arranged in the central region 21 in the regenerative refrigerator 1 A of the above first embodiment.
two types of regenerative materials 50 a and 50 b are used as the regenerative material 50 having a peak of the specific heat at 30K or less.
the regenerative materials 50 a and 50 b are laminated via a separating plate 35 .
HoCu 2 being the magnetic regenerative material used in the first embodiment is used as the first regenerative material 50 a, which is positioned on the upper side.
GOS Cd 2 O 2 S
the second regenerative material 50 b being a ceramics regenerative material is used as the second regenerative material 50 b, which is positioned on the lower side.
GOS has a specific heat of about two times of that of HoCu 2 in an ultralow temperature region of 4K to 5K. Therefore, the first and second regenerative materials 50 a and 50 b are arranged in regenerative material 50 b made of GOS is provided on the low temperature side of the position of providing the first magnetic regenerative material 50 a. Then, it is possible to obtain a higher efficiency of accumulating cooling in the second embodiment than in the first embodiment.
GOS is used as the second regenerative material 50 b, it is possible to use another regenerative material having a high specific heat peak in the ultralow temperature such as GAP (GdAlO 3 ) instead of GOS.
GAP GaAlO 3
FIG. 5 schematically illustrates a regenerative refrigerator 1 C of the third embodiment.
a two-stage regenerative refrigerator 1 A including two sets of the displacer, the cylinder, the regenerator and so on is illustrated.
this patent application is not limited to the two-stage regenerative refrigerator.
the magnetic regenerative material 62 is provided in the central region 21 of a single-stage regenerative refrigerator.
a nonmagnetic regenerative material 64 is provided in the peripheral region 22 around the central region 21 .
the regenerative materials 62 and 64 of two different types are used.
the regenerative material 62 having a high specific heat is filled in the central region 21
the regenerative material 64 having a low specific heat is filled in the peripheral region 22 to thereby perform an effect similar to the first embodiment.
the temperature inside the single-stage regenerative refrigerator 10 is higher than the temperature inside a multi-stage regenerative refrigerator. Therefore, in the single-stage regenerative refrigerator 10 , the regenerative material provided in the central region 21 is not limited to a magnetic regenerative material and may be a material having a lower specific heat than that of the magnetic regenerative material. Further, the nonmagnetic regenerative material other than the magnetic regenerative material may be filled in the central region 21 .
a ratio between cross-sectional areas of the central and peripheral regions is appropriately selected depending on the capability and the size of the refrigerator. It is preferable that the central region occupies from about 50% to about 95%.
FIG. 6 schematically illustrates a regenerative refrigerator of the fourth embodiment.
the regenerative refrigerator 1 D is separated into the high and low temperature sides by providing a separating member 36 inside the second stage regenerator 26 .
the nonmagnetic regenerative material 40 fills the region on the high temperature side (hereinafter, a “high temperature region” 26 a ), and the magnetic regenerative material 42 fills the region on the low temperature side (hereinafter, a “low temperature region” 26 b ). Therefore, in the low temperature region 26 b of the second regenerator 26 , the magnetic regenerative material 42 is provided in both of the central region 21 and the peripheral region 22 .
a filler 44 A is provided in the peripheral region 22 of the magnetic regenerative material 42 on the low temperature side.
FIG. 7A is an enlarged view of the filler 44 A.
the filler 44 A is formed of a plate material made of copper, a copper alloy or the like having high heat conductivity.
the filler 44 A is in a ring shape (an annular shape) with a central hole 45 formed in the center.
the diameter of the central hole 45 is substantially the same as the diameter of the central region 21 .
the outer diameter of the filler 44 A is determined so that the filler 44 A can be installed inside the second stage regenerator 26 .
plural through holes 46 are opened in the filler 44 A.
8 pairs of (two) through holes of the through holes 46 are opened in a radial pattern.
the diameters of the through holes 46 are set to be larger than a particle diameter of the magnetic regenerative material 42 .
the above filler 44 A is provided inside the second stage regenerator 26 . At this time, the filler 44 A is provided inside the second stage regenerator so as to be embedded in the regenerative material 42 . Within the fourth embodiment, three sheets of the fillers 44 A are piled with a predetermined gap inside the magnetic regenerative material 42 . However, the number of the fillers 44 A filling the inside of the magnetic regenerative material 42 is not limited to the above and can be appropriately selected.
the central hole 45 is opened in the filler 44 A.
the filler 44 A is provided substantially in the peripheral region 22 .
the filling rate of the magnetic regenerative material inside the low temperature region 26 b is described.
the filler 44 A is provided (embedded). Therefore, the filling amount of the magnetic regenerative material 42 is decreased by the volume of the filler 44 A.
the filling rate of the magnetic regenerative material 42 in the central region 21 inside the low temperature region 26 b is higher because the central hole 45 is opened in the center of the filler 44 A corresponding to the central region 21 . Meanwhile, the filling rate of the magnetic regenerative material 42 in the peripheral region 22 is lower than in the central region 21 because the filler 44 A exists in the peripheral region 22 .
the filling rate of the magnetic regenerative material 42 in the central region 21 is greater than the filling rate of the magnetic regenerative material 42 in the peripheral region 22 inside the low temperature region 26 b. Therefore, inside the low temperature region 26 b, the specific heat of the central region 21 is larger than the specific heat of the peripheral region 22 .
the filling amount of the magnetic regenerative material 42 can be reduced without reducing a cooling efficiency of the second stage regenerator 26 of the regenerative refrigerator 1 D of the fourth embodiment.
FIGS. 7B and 7C illustrate modified examples to the filler 44 A illustrated in FIG. 7A .
a filler 44 B illustrated in FIG. 7B is formed of a metallic mesh.
the structure of the metallic mesh is not specifically limited and can be appropriately selected in response to the specific heat and the filling rate of the desirable regenerative material.
a filler 44 C illustrated in FIG. 7C is formed so that radiating openings 47 extend from the central hole 45 instead of the through holes 46 opened in the filler 44 A.
the radiating opening 47 is shaped like a trapezoid, of which lower base longer than the upper base is connected with the central hole 45 .
the materials of the fillers 44 B and 44 C are preferably copper or a copper alloy having a high heat conductivity such as the filler 44 A.
the outer shape of the fillers 44 B and 44 C of the modified example illustrated in FIGS. 7B and 7C are like rings
the outer shape of the filler is not limited to the shape of a ring.
the outer shape of the filler may be a sphere, a cylindrical column, a rectangular solid, or the like.

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Engineering & Computer Science (AREA)
Physics & Mathematics (AREA)
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Thermal Sciences (AREA)
General Engineering & Computer Science (AREA)
Containers, Films, And Cooling For Superconductive Devices (AREA)
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US13/871,100 2012-07-20 2013-04-26 Regenerative refrigerator Abandoned US20140020407A1 (en)

Priority Applications (1)

Application Number	Priority Date	Filing Date	Title
US15/672,449 US10203135B2 (en)	2012-07-20	2017-08-09	Regenerative refrigerator

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
JP2012161531A JP5889743B2 (ja)	2012-07-20	2012-07-20	蓄冷式冷凍機
JP2012-161531		2012-07-20

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US15/672,449 Active US10203135B2 (en)	2012-07-20	2017-08-09	Regenerative refrigerator

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Also Published As

Publication number	Publication date
CN103574961B (zh)	2016-06-29
US10203135B2 (en)	2019-02-12
US20170336107A1 (en)	2017-11-23
JP2014020716A (ja)	2014-02-03
JP5889743B2 (ja)	2016-03-22
CN103574961A (zh)	2014-02-12

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