US20160252280A1 - Stirling refrigerator - Google Patents

Stirling refrigerator Download PDF

Info

Publication number: US20160252280A1
Authority: US; United States
Prior art keywords: heat; stirling refrigerator; mount; casing; piston
Prior art date: 2015-02-26
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

US15/051,815

Other languages

English (en)

Inventor

Takeshi Suzuki

Mineyuki Inoue

Jun TANIKAWA

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.)

Twinbird Corp

Original Assignee

Twinbird Corp

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.)

2015-02-26

Filing date

2016-02-24

Publication date

2016-09-01

2016-02-24 Application filed by Twinbird Corp filed Critical Twinbird Corp

2016-02-24 Assigned to TWINBIRD CORPORATION reassignment TWINBIRD CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: INOUE, MINEYUKI, SUZUKI, TAKESHI, TANIKAWA, JUN

2016-09-01 Publication of US20160252280A1 publication Critical patent/US20160252280A1/en

Status Abandoned 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
- F25B31/00—Compressor arrangements
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type
- 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
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/0226—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with an intermediate heat-transfer medium, e.g. thermosiphon radiators
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0275—Arrangements for coupling heat-pipes together or with other structures, e.g. with base blocks; Heat pipe cores
- 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
- F25B2309/001—Gas cycle refrigeration machines with a linear configuration or a linear motor

Definitions

the present invention relates to a Stirling refrigerator, particularly to a free-piston type Stirling refrigerator in which an electromagnetic reciprocating drive mechanism and a compression chamber are positioned comparatively close to each other.
stator of the driving unit comprising a laminated core and an electromagnetic coil.
the displacer starts reciprocating with a predetermined phase difference relative to the piston.
the compression chamber provided between the piston and the displacer, is brought into a high temperature state while the expansion chamber, located on the other side of the compression chamber across the displacer, is brought into a low-temperature state.
the refrigerator is thus capable of cooling a cooling target.
a heat is generated in the compression chamber, it needs to be cooled.
Casings for such Stirling refrigerators are generally formed of a comparatively thick stainless steel material.
One of the reasons for employing such material is because it is necessary to make a leakage of helium less likely to occur since helium is often used as an operating gas encapsulated in the casing of such Stirling refrigerator and helium is the nearest to the ideal gas and prone to be leaked.
Other reasons therefor are because the casing needs to be manufactured from a metal capable of withstanding a high pressure as an operating gas is encapsulated therein at a high pressure; and stainless steel is relatively inexpensive and has an excellent workability and corrosion resistance.
Such Stirling refrigerators generate heat not only in a compression chamber but also in an electromagnetic reciprocating drive mechanism.
the heat generated in the electromagnetic reciprocating drive mechanism originates from Joule heat (or copper loss) caused by an electric current flowing through the electromagnetic coil, as well as a loss at a laminated core (or iron loss).
Joule heat or copper loss
a loss at a laminated core or iron loss
the casing is generally formed of a stainless steel material not so high in thermal conductivity. For this reason, and along with the material being comparatively thick, there have been concerns about the electromagnetic reciprocating drive mechanism being unable to be cooled down to the full extent. This problem has been a main factor hindering the improvement of the cooling capacity of Stirling refrigerators.
a first aspect of the present invention is a Stirling refrigerator including:
a casing having a cylindrical portion and a body portion
a cylinder provided with a mount housed within the casing, the mount formed of a metal exhibiting high thermal conductivity;
stator of an electromagnetic reciprocating drive mechanism the stator held on the mount and arranged within the body portion;
the casing is partially formed with a heat-conduction block formed of a metal exhibiting high thermal conductivity, and the heat-conduction block is thermally in contact with the mount.
a second aspect of the present invention is a Stirling refrigerator as set forth in the first aspect wherein the heat-conduction block is provided on the outside of the compression chamber defined between the piston and the displacer.
a third aspect of the present invention is a Stirling refrigerator as set forth in the second aspect wherein on the body portion is formed at least one through-hole through which a heat pipe or thermosiphon is inserted into the body portion, and a gap provided between the through-hole and the heat pipe or thermosiphon is sealed.
a heat generated at the stator of the electromagnetic reciprocating drive mechanism is allowed to be released to the outside of the casing through the mount and the heat-conduction block 4 that are formed of a metal having a high thermal conductivity.
the electromagnetic reciprocating drive mechanism can be fully cooled, thus enhancing the cooling capacity of the Stirling refrigerator.
the heat-conduction block is provided on the outside of the compression chamber defined between the piston and the displacer, whereby a heat generated in the compression chamber can also be released through the heat-conduction block at the same time.
the body portion is formed at least one through-hole through which a heat pipe or a thermosiphon is inserted into the body portion, while a gap between the through-hole and the heat pipe (or thermosiphon) is sealed.
FIG. 1 is a vertical cross-sectional view showing a Stirling refrigerator of a first example of the present invention.
FIG. 2 is an enlarged cross-sectional view of a main section of the Stirling refrigerator shown in FIG. 1 .
numeral 1 denotes a casing forming an outer hull of the Stirling refrigerator.
the casing 1 includes: a cylindrical portion 2 and a body portion 3 that have a substantially cylindrical shape; a heat-conduction block 4 having a substantially cylindrical shape with a lower end thereof formed into a flange shape; and an annular block 5 having an annular plate shape.
the cylindrical portion 2 is integrally formed with a main body 2 A and a distal portion 2 B, and is open at a lower end thereof.
the cylindrical portion 2 is formed entirely of a metal such as stainless steel.
the body portion 3 has a substantially U-shaped, bottomed cylindrical shape when viewed in a longitudinal section, and is open at an upper end thereof. On a main body portion 3 A are formed a plurality of through-holes 3 B for inserting later-described heat pipes 36 thereinto.
the body portion 3 is formed entirely of a metal such as stainless steel.
the heat-conduction block 4 is integrally formed of: a block body 4 A having a substantially cylindrical shape whose top and bottom are open; and a flange portion 4 B extended horizontally in an outer circumferential direction from a lower end of the block body 4 A.
An inner circumference of the lower end of the block body 4 A is formed with a chamfer 4 C.
an outer circumference of the flange portion 4 B is formed with a vertically two-step structure in which a lower step 4 E is protruded outwardly of an upper step 4 D toward an outer circumferential direction.
the heat-conduction block 4 is formed of a metal, such as copper, exhibiting a higher thermal conductivity and strength as compared to a metal such as stainless steel constituting the body portion 3 .
the annular block 5 has a substantially annular plate shape in a planar view.
An inner circumference of the annular block 5 is formed with upper and lower two steps in which an upper step 5 A is protruded inwardly of a lower step 5 B in an inner circumferential direction. These upper and lower steps 5 A, 5 B are respectively abutted on and joined to the upper and lower steps 4 D, 4 E through brazing.
An outer circumference 5 C of the annular block 5 is welded to an inner surface of the body portion 3 .
the annular block 5 is formed entirely of stainless steel. Alternatively, the welded portion of the heat-conduction block 4 and the annular block 5 may be formed into another shape.
An upper end surface 3 C of the body portion 3 , an upper surface 5 D of the annular block 5 and upper surface 4 F of the flange portion 4 B are flush with each other. Further, a lower surface 5 E of the annular block 5 and a lower surface 4 G of the flange portion 4 B are flush with each other. Furthermore, a lower end portion of the cylindrical portion 2 is joined to an inner circumference of an upper end portion of the heat-conduction block 4 through brazing.
a cylinder 7 extending up to the inside of the body portion 3 is coaxially inserted into the cylindrical portion 2 .
An extended cylinder portion 6 separate from the cylinder 7 , is coaxially connected to a cylinder distal portion 7 A.
the cylinder 7 is integrally formed with later-described mounts 26 , 27 and connecting arms 30 by casting, such as die casting or the like, using a metal such as aluminum, followed by subjecting inner and outer peripheral surfaces, etc. of the cylinder 7 to cutting work after casting.
a displacer 8 is slidably provided within the cylinder distal portion 7 A and the extended cylinder portion 6 in the axial direction. Also, an expansion chamber E is provided between a distal end portion 8 A of the displacer 8 and the distal portion 2 B of the cylindrical portion 2 . Inside and outside of the extended cylinder portion 6 are communicated with each other via a space 9 .
a regenerator 10 is provided between the inner circumference of the main body 2 A of the cylindrical portion 2 and the outer circumference of the extended cylinder portion 6 . Further, on the cylinder 7 is formed a communication hole 11 for allowing the inside of the cylinder 7 to communicate with the outside thereof.
a heat absorbing fin 12 is provided between the inner circumference of the distal portion 2 B and the outer circumference of the distal end of the extended cylinder portion 6
a heat dissipating fin 13 is provided between the outer circumference of the cylinder 7 and the inner circumference of the cylindrical portion 2 , in a position between the regenerator 10 and the communication hole 11 .
a piston 15 is provided on the inside of the cylinder base portion 7 B of the cylinder 7 within the body portion 3 in a manner capable of sliding therein in the axial direction.
An electromagnetic reciprocating drive mechanism 16 that serves as a driving mechanism for reciprocating the piston 15 includes:
a mover 17 of a short cylindrical shape provided on the outside of the cylinder base portion 7 B in a manner extending coaxially therewith;
a ring-shaped electromagnetic coil 19 provided adjacent to the outer circumference of the permanent magnet 18 ;
the electromagnetic coil 19 is wound around a stator 24 , while the stator 24 is integrated with the electromagnetic coil 19 .
a lower part 15 A of the piston 15 located at a lower end part of the piston 15 is connected to a bottom part 17 A of the mover 17 located at a bottom thereof.
the piston 15 and the mover 17 are structured so as to work with each other.
the lower part 15 A of the piston 15 is connected to a first flat spring 21 for controlling a movement of the piston 15 .
a rod 22 for controlling the movement of the displacer 8 is connected to a second flat spring 23 .
This rod 22 extends in a manner penetrating through the piston 15 .
a pair of the first flat spring 21 and the second flat spring 23 they are provided below the cylinder 7 within the body portion 3 , with the second flat spring 23 being positioned lower than the first flat springs 21 .
the aforesaid mount 26 Between the cylinder distal portion 7 A and the cylinder base portion 7 B is integrally formed the aforesaid mount 26 in a manner coaxial therewith. At a lower end of the mount 26 is integrally formed the aforesaid mount 27 of a flange type extending in an outer circumferential direction.
An upper surface 27 A of the mount 27 is formed into a flat shape so as to be thermally in contact or abutted with a lower surface 4 G of the flange portion 4 B of the heat-conduction block 4 . Further, a lower surface 27 B of the mount 27 is formed so as to be abutted with an upper surface of the stator 24 constituting the electromagnetic reciprocating drive mechanism 16 . Furthermore, on the lower surface of the stator 24 is abutted a fixation ring 28 , thus sandwiching the stator 24 between the fixation ring 28 and the mount 27 . This way, the stator 24 , and eventually the electromagnetic coil 19 that is integrated with the stator 24 , are fixed to the mount 27 .
a plurality of the connecting arms 30 extend downwardly in a direction substantially parallel with an axial direction of the cylinder 7 . Note that the plurality of connecting arms 30 are integrally formed with the mount 27 .
Distal end surfaces 30 B of the connecting arms 30 are formed on the same plane in a manner orthogonally crossing the axial direction of the cylinder 7 .
On each of the distal end surfaces 30 B is formed a screw hole 30 C having an internal thread in parallel with the axial direction of the cylinder 7 .
the aforesaid first flat spring 21 contacts the distal end surfaces 30 B.
the first flat spring 21 is sandwiched and supported between the connecting arms 30 and respective spacers 31 while being in contact with the distal end surfaces 30 B.
each spacer 31 employs such a structure that its main body 31 A has a regular hexagonal pillar shape; one end thereof has a male screw 31 B formed coaxially with the main body 31 A so as to be screwed into the internal thread 30 C; the other end surface 31 C thereof has a screw hole 31 D having an internal thread formed coaxially with the main body 31 A. Then, by screwing the male screws 31 B provided at one end of the spacers 31 into the respective screw holes 30 C of the connecting arms 30 via the screw holes 21 A formed in the first flat spring 21 , the first flat spring 21 is sandwiched between the connecting arms 30 and the spacers 31 . At this moment, since the spacers 31 have a regular hexagonal pillar contour, it is easy to attach the spacers 31 to the respective connecting arms 30 by tightening with a wrench or the like.
the spacers 31 With the spacers 31 being attached to the respective connecting arms 30 , the spacers 31 are formed flush with each other such that the other end surfaces 31 C thereof orthogonally intersect with the axis of the cylinder 7 , and the second flat spring 23 comes in contact with the other end surfaces 31 C. With the second flat spring 23 being in contact with the other end surfaces 31 C, it is fixed to the spacer 31 by fitting the screws 32 into the internal thread of the screw holes 31 D via the screw holes 23 A formed in the second flat spring 23
each of these heat pipes 36 has a structure integrally formed with: a basal portion 36 A arranged within the body portion 3 in parallel with an axial direction of the piston 15 ; and an arm portion 36 B protruded in parallel through the through-holes 3 B formed on the main body portion 3 A toward the outside of the body portion 3 , or of the casing 1 . Between the heat pipe 36 and the through-hole 3 B is provided a gap 37 , which is sealed by a brazing joint 38 .
the heat pipes 36 are well known in the art, yet just to make sure, they will be described herein below.
the heat pipes 36 are made of pipes formed of a metal such as copper having high thermal conductivity.
the pipes are evacuated inside and an operating fluid is encapsulated therein.
On the inner wall of the heat pipes 36 are formed wicks, or capillary structures (not shown).
the basal portions 36 A are arranged in a position opposed to the electromagnetic coil 19 and function as heat receiving portions for receiving a heat generated, due to the current flow, from the electromagnetic coil 19 .
the arm portions 36 B function as heat dissipating portions for releasing a heat received at the basal portions 36 A to the outside of the casing 1 in which the temperature outside of the casing 1 is lower than the temperature within the casing 1 .
the basal portions 36 A will be heated by a heat generated from the electromagnetic coil 19 , and then the operating fluid inside the basal portions 36 A will be evaporated. The evaporated operating fluid will be then transferred to the arm portions 36 B of a lower temperature, and will be cooled, condensed and liquefied there. On the inner wall of the heat pipes 36 are formed wicks, which will bring the operating fluid liquefied at the arm portions 36 B back to the basal portions 36 A by so called capillary action.
the liquefied operating fluid since the liquefied operating fluid is transported through the capillary action, the liquefied operating fluid is allowed to be refluxed from the arm portions 36 B to the basal portions 36 A, irrespective of the posture of the heat pipes 36 , or that of the Stirling refrigerator provided with the heat pipes 36 . In this way, the heat pipes 36 have a high thermal conductivity through circulating an operation fluid.
each of the heat pipes 36 is preferably to be arranged in between the plurality of connecting arms 30 in practical use.
the heat pipes 36 are capable of releasing to the outside of the casing 1 not only the heats generated at the electromagnetic reciprocating drive mechanism 16 but also the heats of the operating fluid inside the body portion 3 heated by the heat generated in the electromagnetic reciprocating drive mechanism 16 and/or the compression chamber C.
thermosiphon (not shown) in place of the heat pipe 36 .
thermosiphons are also well known in the art, yet just to make sure, they will be described herein below.
the thermosiphons are made of pipes formed of a high thermal conductive metal such as copper.
the pipes are evacuated inside and an operating fluid is encapsulated therein.
an operating fluid is encapsulated therein.
on the upper and lower portion of the thermosiphon are respectively provided a heat receiving portion and a heat dissipating portion.
the operating fluid encapsulated therein will be heated at the heat receiving portion and then vaporized to move upward through the thermosiphons.
the vaporized operating fluid will then be cooled, condensed and liquefied at the heat dissipating portion.
thermosiphon As for such thermosiphon, there may be employed a single pipe thermosiphon of a type having no wick structure (or no capillary structure), or a so-called looped thermosiphon provided with: a pipe through which the vaporized operating fluid travels upwardly; and a pipe through which the liquefied operating fluid moves downwardly.
a numeral 33 denotes a vibration absorbing unit 33 provided at a lower part of the casing 1 , in which a plurality of flat springs 34 and a balance weight 35 are coaxially arranged such that the flat springs 34 are stacked on the balance weight 35 through coupling members arranged on the axial line of the cylinder 7 .
This vibration absorbing unit 33 serves to absorb vibration of the casing caused by the reciprocating movements of the piston 15 and the displacer 8 .
an alternating current of a predetermined frequency will be applied to the electromagnetic coil 19 of the stator 24 of the electromagnetic mechanism 16 from a power source (not shown) provided outside the casing 1 via a driving circuit (not shown) and a power cord.
a driving circuit not shown
a power cord By applying an alternating current to the electromagnetic coil 19 this way, an alternating magnetic field will be generated from the electromagnetic coil 19 and be concentrated around the stator 24 .
this alternating magnetic field generates a force to reciprocate the mover 17 along the axial direction thereof. Due to this force, the piston 15 , connected to the mover 17 to which the permanent magnet 18 is fixed, will start reciprocating in the cylinder 7 along the axial direction thereof.
the heat-conduction block 4 is in contact with the heat dissipating fin 13 and the mount 27 . For this reason, there can be also received a heat conducted from the compression chamber C to the heat dissipating fin 13 and/or the mount 27 in an efficient manner. Further, the heat-conduction block 4 is allowed to receive a heat conducted from the electromagnetic reciprocating drive mechanism 16 to the mount 27 in an efficient manner. The heat-conduction block 4 serves to release heats, received from above mentioned parts, to the outside of the casing 1 having lower temperature. In this way, cooling capacity of the Stirling refrigerator can be enhanced.
the Stirling refrigerator of the present example includes:
a casing 1 having a cylindrical portion 2 and a body portion 3 ;
a cylinder provided with a mount 27 housed within the casing 1 , the mount 27 formed of a metal exhibiting high thermal conductivity;
stator of an electromagnetic reciprocating drive mechanism 16 the stator held on the mount 27 and arranged within the body portion 3 ;
the casing 1 is partially formed with a heat-conduction block 4 formed of a metal exhibiting favorable thermal conductivity and the heat-conduction block 4 is thermally in contact with the mount 27 .
thermosiphons are inserted into the body portion 3 .
Gaps 37 provided between the through-holes 3 B and the heat pipes 36 (or thermosiphons) are sealed.
the present invention shall not limited to the example described above and various modifications are possible within the scope of the gist of the present invention.
tubular shaped heat pipes are employed in the foregoing example, there may be employed a heat pipe of any other shape, such as a sheet-shaped heat pipe.

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

US15/051,815 2015-02-26 2016-02-24 Stirling refrigerator Abandoned US20160252280A1 (en)

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
JP2015036985A JP2016161140A (ja)	2015-02-26	2015-02-26	スターリング冷凍機
JP2015-036985		2015-02-26

Publications (1)

Publication Number	Publication Date
US20160252280A1 true US20160252280A1 (en)	2016-09-01

Family

ID=55661091

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
US15/051,815 Abandoned US20160252280A1 (en)	2015-02-26	2016-02-24	Stirling refrigerator

Country Status (3)

Country	Link
US (1)	US20160252280A1 (ja)
EP (1)	EP3062039A1 (ja)
JP (1)	JP2016161140A (ja)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CN107061049A (zh) *	2017-02-23	2017-08-18	宁波华斯特林电机制造有限公司	一种带导冷结构的斯特林电机
US10753653B2 (en) *	2018-04-06	2020-08-25	Sumitomo (Shi) Cryogenic Of America, Inc.	Heat station for cooling a circulating cryogen
CN113028673A (zh) *	2019-12-24	2021-06-25	珍巴多工业股份有限公司	自由活塞式斯特林制冷机
CN115143659A (zh) *	2022-06-29	2022-10-04	宁波钜心低温科技有限公司	一种斯特林冷机
US11473524B2 (en) *	2019-01-25	2022-10-18	Twinbird Corporation	Reciprocating motion engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CN112885494B (zh) *	2021-01-26	2022-08-02	哈尔滨工程大学	一种基于星型斯特林发动机的反应堆电源***

Citations (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US4295067A (en) *	1978-03-09	1981-10-13	Robert Bosch Gmbh	Cooling apparatus for electrical machinery
US20090193805A1 (en) *	2007-08-22	2009-08-06	Global Cooling Bv	Stirling cycle engine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
JPH01155150A (ja) *	1987-12-11	1989-06-19	Mitsubishi Electric Corp	冷凍機
JP2000337725A (ja) *	1999-05-25	2000-12-08	Twinbird Corp	スターリングサイクル冷凍機の駆動機構
JP2001355513A (ja) *	2000-06-13	2001-12-26	Twinbird Corp	スターリングサイクル機関
US6931863B2 (en) *	2000-08-22	2005-08-23	Sharp Kabushiki Kaisha	Stirling refrigerator
JP3769751B2 (ja) *	2003-02-19	2006-04-26	ツインバード工業株式会社	スターリングサイクル機関
JP2009133513A (ja) *	2007-11-29	2009-06-18	Sharp Corp	スターリングサイクル装置

2015
- 2015-02-26 JP JP2015036985A patent/JP2016161140A/ja active Pending
2016
- 2016-02-24 US US15/051,815 patent/US20160252280A1/en not_active Abandoned
- 2016-02-26 EP EP16157607.9A patent/EP3062039A1/en not_active Withdrawn

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US4295067A (en) *	1978-03-09	1981-10-13	Robert Bosch Gmbh	Cooling apparatus for electrical machinery
US20090193805A1 (en) *	2007-08-22	2009-08-06	Global Cooling Bv	Stirling cycle engine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CN107061049A (zh) *	2017-02-23	2017-08-18	宁波华斯特林电机制造有限公司	一种带导冷结构的斯特林电机
US10753653B2 (en) *	2018-04-06	2020-08-25	Sumitomo (Shi) Cryogenic Of America, Inc.	Heat station for cooling a circulating cryogen
US11649989B2 (en)	2018-04-06	2023-05-16	Sumitomo (Shi) Cryogenics Of America, Inc.	Heat station for cooling a circulating cryogen
US11473524B2 (en) *	2019-01-25	2022-10-18	Twinbird Corporation	Reciprocating motion engine
CN113028673A (zh) *	2019-12-24	2021-06-25	珍巴多工业股份有限公司	自由活塞式斯特林制冷机
US11255581B2 (en) *	2019-12-24	2022-02-22	Twinbird Corporation	Free piston Stirling refrigerator
CN115143659A (zh) *	2022-06-29	2022-10-04	宁波钜心低温科技有限公司	一种斯特林冷机

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Publication number	Publication date
EP3062039A1 (en)	2016-08-31
JP2016161140A (ja)	2016-09-05

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