WO2002031418A1 - Echangeur thermique et refrigerateur comportant cet echangeur thermique - Google Patents

Echangeur thermique et refrigerateur comportant cet echangeur thermique Download PDF

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Publication number
WO2002031418A1
WO2002031418A1 PCT/JP2001/008153 JP0108153W WO0231418A1 WO 2002031418 A1 WO2002031418 A1 WO 2002031418A1 JP 0108153 W JP0108153 W JP 0108153W WO 0231418 A1 WO0231418 A1 WO 0231418A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
heat
refrigerator
base
exchanger according
Prior art date
Application number
PCT/JP2001/008153
Other languages
English (en)
Japanese (ja)
Inventor
Takashi Nishimoto
Original Assignee
Sharp Kabushiki Kaisha
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sharp Kabushiki Kaisha filed Critical Sharp Kabushiki Kaisha
Publication of WO2002031418A1 publication Critical patent/WO2002031418A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • F25D17/062—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators
    • F25D17/065—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators with compartments at different temperatures
    • 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
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D23/00—General constructional features
    • F25D23/003—General constructional features for cooling refrigerating machinery
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
    • F25D2400/04—Refrigerators with a horizontal mullion

Definitions

  • the present invention relates to a heat exchanger for extracting cold generated by a cooler such as a Stirling refrigerator and a refrigerator including the same.
  • refrigeration systems used in refrigerators and the like use a vapor compression refrigeration cycle.
  • This refrigeration system mainly uses chlorofluorocarbon and its alternatives as refrigerants, but since these refrigerants have been known to adversely affect the global environment, such as causing ozone layer depletion and global warming, they have been used worldwide. Its use is restricted.
  • the low temperature part (cold head) of the Stirling refrigerator absorbs heat from the air in the refrigerator through the low-temperature side heat exchanger due to the expansion of the working medium.
  • the inside is cooled.
  • the high temperature part ( ⁇ ohm head) of the Stirling refrigerator the working medium is compressed and radiated to the air outside the refrigerator through the high temperature side heat exchanger.
  • this Stirling refrigerator does not use the latent heat of the working medium, unlike the conventional refrigerator using a vapor compression refrigeration cycle. Therefore, in order to obtain the required refrigeration capacity of several hundreds of liters for the refrigerator, the heat transfer area between the cold head and the warm head is small, and heat transfer cannot be performed efficiently. The input increases.
  • this refrigerator has a Stirling refrigerator 6 housed in a machine room provided at an upper portion of the main body 1.
  • reference numeral 20 denotes a cylinder
  • 21 denotes a power piston
  • 22 denotes a display piston
  • 23 denotes a reciprocating mechanism for reciprocating each of the bistons 21 and 22 with a predetermined phase difference.
  • a rotating body 231 which is provided with rotational power by a drive motor (not shown), and a pair of biscuit openings 23, 23 and 33, are formed.
  • the compression space 20 a and the expansion space 20 b formed in the cylinder 20 communicate with each other via a regenerator 24 to form a closed circuit, and the working space in the closed circuit includes helium gas and nitrogen. It is filled with a working medium such as gas.
  • the compression space 20 a of the cylinder 20 is the worm head 61
  • the expansion space 20 b is the cold head 62.
  • the warm head 61 is provided with a high-temperature side heat exchanger 7. Cooling in the refrigerator is performed as follows. That is, the heat pipe 13 provided as a low-temperature side heat exchanger facing the cold head 62 extends into the refrigerator and is located in the cold air duct 9. Further, the heat pipe 13 is provided with fins 10 2, 0 , '.
  • the cold generated in the cold head 6 2 is conveyed into the refrigerator by the refrigerant filled in the heat pipe 13, It is supplied to the air in the refrigerator by heat exchange via the fins 102.
  • air in the refrigerator circulated by the cool air fan 11 flows, and the inside of the refrigerator is cooled to a predetermined temperature by supplying cold heat.
  • cold heat is the negative heat obtained by endotherm.
  • a heat pipe 13 is provided at the high temperature end of the heat pipe 13 with a heat exchanger 102 for exchanging heat with the airflow in the cold air duct 9, and a heat exchanger for extracting cold heat from the cold head 62 at the low temperature end. (Not shown).
  • a heat exchanger 102 for exchanging heat with the airflow in the cold air duct 9
  • a heat exchanger for extracting cold heat from the cold head 62 at the low temperature end.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide a heat exchanger having a simple configuration, capable of efficiently extracting cold heat, and a refrigerator including the same.
  • a fin attached to a surface of the base has a plate-like base, and a part of the base is used as a cooling unit that is cooled from the outside.
  • a heat exchanger a portion of which is located outside the cooling section of the substrate, includes a medium that becomes a gas and a liquid according to temperature, and includes a medium that evaporates and condenses.
  • a heat transfer mechanism for transferring heat of a portion located outside the cooling unit toward the cooling unit;
  • the heat of the portion of the substrate located outside the cooling section is transferred toward the cooling section (transferring the cold heat in the opposite direction). This is performed by using latent heat accompanying the phase change of the medium. Therefore, the part of the base other than the cooling part directly cooled from the outside is efficiently cooled, and as a result, the entire bushing is efficiently cooled.
  • the heat transfer mechanism includes a pipe in which the medium is sealed and attached to the base.
  • This pipe is a so-called heat pipe, and the above-described heat exchanger can be obtained by simply attaching the independent heat pipe to the base. .
  • the base may have a groove on the surface, and the pipe may be arranged in the groove on the surface of the base.
  • the contact area between the heat pipe and the base can be increased, and the distance between the surface of the base on which the fin is mounted and the heat pipe is shortened, thereby increasing the cooling efficiency of the fin.
  • the base may have a space inside, the medium may be sealed in the base, and the base itself may be the heat transfer mechanism. With this configuration, the medium can be brought into contact with a wide area of the base, and the distance between the surface of the base on which the fins are attached and the inner surface of the base with which the medium comes into contact can be shortened. Cooling efficiency is increased.
  • the above heat exchanger may be used in an arrangement in which the portion of the base body to which heat is transferred by the heat transfer mechanism toward the cooling unit is located below the cooling unit. In this use, the medium is condensed above and evaporates below, thereby promoting circulation of the medium.
  • a storage chamber for storing articles, a circulation path through which the air in the storage chamber returns to the storage chamber, and a cooler for cooling the air passing through the circulation path.
  • a cooling box provided with the heat exchanger, wherein the heat exchanger is arranged so that the fins are located on the circulation path, and the cooler contacts the cooling unit to cool the cooling unit. Configuration.
  • This cooler can efficiently cool the air passing through the circulation path, and thus can efficiently cool the storage chamber.
  • the containment room can be used as a cold room where water does not freeze or as a freezer room where water freezes.
  • a heat exchanger includes: a contact portion that contacts a cold head of a Stirling refrigerator; and a heat exchanger that is disposed in a direction opposite to the contact portion to promote heat exchange.
  • a heat pipe is provided between the fins. Therefore, the cold generated by the cold head is diffused by the heat pipe and transmitted to the vine.
  • the contact portion if the contact portion is located above the heat pipe, the upper portion of the heat pipe serves as a refrigerant condensing portion, and the lower portion serves as an evaporating portion.
  • the refrigerant condensed at the upper part of the heat pipe naturally flows down by gravity and reaches the evaporating section.
  • a heat exchanger includes: a contact portion that contacts a cold head of a Stirling refrigerator; and a heat exchanger that is disposed in a direction opposite to the contact portion to promote heat exchange. And a fin is provided between the fins.
  • a natural refrigerant such as carbon dioxide gas such as carbon dioxide, hydrocarbon gas such as propane, butane, and pentane, and ammonia may be used.
  • a refrigerator includes a Stirling refrigerator equipped with the above-described heat exchanger.
  • This heat exchanger is installed in a cool air duct where the air in the refrigerator circulates, and the air in the refrigerator is passed between the fins.
  • the cold generated by the cold head of the Stirling refrigerator is passed through the heat exchanger. To the air in the refrigerator.
  • FIG. 1 is a longitudinal sectional view showing a schematic configuration of an embodiment of a refrigerator according to the present invention.
  • FIG. 2 is a perspective view showing the configuration of the first embodiment of the heat exchanger according to the present invention.
  • FIG. 3 is a horizontal sectional view showing the configuration of the second embodiment of the heat exchanger according to the present invention.
  • FIG. 4 is a vertical sectional view showing the configuration of the second embodiment of the heat exchanger according to the present invention.
  • FIG. 5 is a perspective view showing another configuration of the fin of the heat exchanger according to the present invention.
  • FIG. 6 is a perspective view showing still another configuration of the fin of the heat exchanger according to the present invention.
  • FIG. 7 is a longitudinal sectional view showing a configuration of a main part of a conventional refrigerator. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1 is a schematic sectional view of the refrigerator.
  • 1 is the main body
  • 2 is the heat insulating material
  • 3 is the opening / closing door
  • 4 is the temperature inside the refrigerator
  • This is a partition plate for separating refrigerator compartment 1a, vegetable compartment 1b, and freezer compartment 1c.
  • Reference numeral 5 denotes a machine room provided above the main body 1 and communicated with the outside of the refrigerator
  • reference numeral 6 denotes a Stirling refrigerator installed in the machine room 5.
  • a high-temperature side heat exchanger 7 is attached to the warm head 61 of the Stirling refrigerator 6.
  • the heat generated in the worm head 61 is forcibly discharged to the outside of the refrigerator by the cooling fan 8 via the high-temperature heat exchanger 7.
  • the cold head 62 faces the upper part of the cold air duct 9 arranged along the back of the main body 1, and the low-temperature side heat exchanger 10 is attached to the tip. Air in the refrigerator is circulated in the cool air duct 9 by the cool air fan 11, and the cold generated in the cold head 62 is exchanged by the heat exchange through the low temperature side heat exchanger 10. Supplied to ⁇
  • FIG. 2 is a perspective view of the present embodiment.
  • the low-temperature side heat exchanger 10 includes a substrate 101 made of aluminum, copper, or the like having good heat conductivity, and a plurality of fins 102 attached to one surface of the substrate 101. It is.
  • the substrate 101 is set upright as shown in this figure.
  • a cold head 62 of a Stirling refrigerator 6 (see FIG. 1) is attached to a contact portion 101 f above the center of the other surface of the substrate 101 by a screw (not shown) or the like.
  • a plurality of grooves 101b extending from the lower side of the contact portion 101f to the lower end of the substrate 101 are formed in the vertical direction, and a coolant is contained in each groove 101b.
  • the heat pipe 13 filled with is press-fitted. As described above, when the groove 101b and the heat pipe 13 are in pressure contact with each other, the heat conductivity is improved by the close contact, so that high heat exchange efficiency can be obtained.
  • the refrigerant is effective in the range of 0 ° C to-40 ° C, which is suitable for use in refrigerators. It is preferable to use a material that does not destroy the ozone layer and has a low global warming potential.
  • carbon dioxide gas such as carbon dioxide
  • hydrocarbon gas such as propane, butane and pentane, and ammonia are suitable.
  • the refrigerant condenses at the upper end near the cold head 62 and moves naturally downward due to gravity. Then, it evaporates at the lower end and moves upward again. In this manner, the circulation of the refrigerant causes the cold heat to diffuse throughout the substrate 101 and to be transmitted to the fins 102.
  • the circulation speed of the refrigerant is increased due to the gravitational acceleration, and the amount of heat transport per unit of the heat pipes 13 is increased. Therefore, in the substrate 101, the cold heat is efficiently transferred to a location far from the cold head 62, and the temperature uniformity of the substrate 101 is improved.
  • a plurality of flat fins 102 are fixed to one surface of the substrate 101 by brazing or the like.
  • Each fin 102 is arranged along the vertical direction similarly to the heat pipe 13. During these fins 1 0 2, air flow flowing through the cold air duct 9 (see FIG. 1) flows out from the lower side to flow from the upper side (in the figure, arrow A) 0
  • the air flow to which the cold heat has been given by the heat exchange in the fins 102 has a higher gas density in the outflow direction, so that natural convection is generated from the gas density difference. Therefore, even if the driving amount of the cool air fan 11 (see Fig. 1) is small, the air flow can be smoothly passed, and the cool air fan 11 requires low power consumption.
  • a plurality of grooves 101b are formed by cutting grooves at predetermined positions on an aluminum plate used as the substrate 101. Also, a plurality of heat pipes 13 in which a refrigerant is sealed in an aluminum pipe having the same diameter as the width of the groove 101 b are prepared, and each of them is press-fitted into the groove 101 b. In other words, in this case, the groove 101b and the heat pipe 13 are brought into pressure contact with each other by a simple operation such as press fitting instead of screwing.
  • a thin aluminum plate is used for the fins 102, and the fins 102 are fixed at predetermined positions on the substrate 101 on which the brazing material has been made. Then, the fins 102 are fixed to the substrate 101 by melting the brazing material in a furnace and then solidifying it again.
  • FIG. 3 shows a cross section in the horizontal direction of the low-temperature side heat exchanger 10 of the present embodiment
  • FIG. 4 shows a cross section in the vertical direction.
  • the low-temperature side heat exchanger 10 has a plurality of flat plate-shaped fins 102 arranged on one surface of a substrate 101 along the vertical direction.
  • a cold head 62 is pressed and fixed to the contact portion 101f at the top of the other surface of the substrate 101.
  • the substrate 101 is placed in the cooling duct 9 (see FIG. 1) in an upright state as shown in this figure.
  • the substrate 101 has a hollow 101c as a heat pipe, and the hollow 101c is filled with a refrigerant from a refrigerant injection port 101d provided at an upper portion.
  • a carbon dioxide gas such as carbon dioxide
  • a hydrocarbon gas such as propane, butane, and pentane
  • ammonia may be used as the refrigerant.
  • a plurality of columns 101 e extend horizontally in the hollow 101 c. Since the static pressure of the hollow 101c becomes higher or lower than the atmospheric pressure depending on the cooling medium and temperature conditions, the column 101e is provided for pressure resistance.
  • the screw hole of the screw 14 used to connect the cold head 62 to the substrate 101 is formed in the column 101 e.
  • the refrigerant condenses near the surface where the cold heads 62 are in close contact, and evaporates near the surface where the fins 102 are attached. Further, since the substrate 101 stands upright, the refrigerant circulates in the vertical direction while receiving gravitational acceleration, and the cold heat is efficiently diffused throughout the substrate 101. Further, in the present embodiment, since the refrigerant circulates through the entire substrate 101 and the cold diffuses, compared to the configuration in which the cold diffuses along the heat pipe 13 (see FIG. 2) as in the first embodiment. Higher heat exchange efficiency is obtained.
  • Two aluminum sheets are prepared as the substrate 101, and the first aluminum sheet is formed into a substantially box shape by press molding. Then, a second aluminum sheet is superimposed on this and brazed around a substantially box shape, and the refrigerant is sealed in the hollow 101c formed therein.
  • a thin aluminum plate is also used for the fins 102, and the fins 102 are fixed at predetermined positions on the substrate 101, which has been brazed. Then, the brazing material is melted in a furnace and then solidified again, whereby the fins 102 are fixed to the substrate 101.
  • the configuration of the fins 102 is not limited to this embodiment as long as the heat conduction performance is high, and may be any configuration.
  • the fins 102 are formed in a lattice shape.
  • the fins 102 are configured in a corrugated shape.
  • the fin 102 shown in FIGS. 5 and 6 has a larger area than the fins 102 of the first and second embodiments, so that higher heat exchange efficiency can be obtained.
  • the refrigerator with the above configuration is simple because only one low-temperature heat exchanger is attached to the cold head of the Stirling refrigerator. Furthermore, since the heat exchange efficiency of the heat exchanger is good, the power consumption of the refrigerator is small.
  • the heat exchanger of the present invention can be used for various devices for cooling gas, such as the illustrated refrigerator.

Abstract

L'invention concerne un échangeur thermique présentant une efficacité d'échange thermique élevée, ainsi qu'un réfrigérateur comportant cet échangeur thermique. Ledit réfrigérateur comprend un appareil de réfrigération de type Stirling (6) ainsi qu'un échangeur thermique (10) venant buter contre la tête de refroidissement (62) de l'appareil de réfrigération. L'échangeur thermique comprend un substrat (101), une ailette (102) installée verticalement sur ce substrat, ainsi qu'un caloduc (13) installé sur la surface dudit substrat. La chaleur issue de parties du substrat autres qu'une partie de butée venant buter contre la tête de refroidissement est dirigée vers la partie de butée par l'intermédiaire du caloduc. Le substrat peut présenter une configuration creuse permettant l'introduction du fluide frigorigène. Par conséquent, il peut lui-même revêtir une fonction de caloduc.
PCT/JP2001/008153 2000-09-29 2001-09-19 Echangeur thermique et refrigerateur comportant cet echangeur thermique WO2002031418A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000300978A JP2002107075A (ja) 2000-09-29 2000-09-29 熱交換器及びそれを備えた冷蔵庫
JP2000-300978 2000-09-29

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Publication Number Publication Date
WO2002031418A1 true WO2002031418A1 (fr) 2002-04-18

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JP (1) JP2002107075A (fr)
TW (1) TW542892B (fr)
WO (1) WO2002031418A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004025198A1 (fr) * 2002-09-11 2004-03-25 Ziquan Zhao Refrigerateur polyvalent a temperature constante comportant un support thermique
CN102168904A (zh) * 2011-01-21 2011-08-31 上海理工大学 一种采用斯特林制冷机的酒柜

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101264086B1 (ko) 2006-08-29 2013-05-14 한라비스테온공조 주식회사 축냉 열교환기

Citations (7)

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JPS61250490A (ja) * 1985-04-26 1986-11-07 スタ−リング・サ−マル・モ−タ−ズ・インコ−ポレ−テツド ヒ−トパイプ
JPH0336468A (ja) * 1989-06-30 1991-02-18 Toshiba Corp 冷却庫
JPH05203377A (ja) * 1991-11-12 1993-08-10 Mitsubishi Electric Corp 平板型ヒートパイプ及び高密度実装モジュール
JPH1062080A (ja) * 1996-08-22 1998-03-06 Mitsubishi Shindoh Co Ltd 配管部材およびヒートパイプ
JPH11201673A (ja) * 1998-01-12 1999-07-30 Furukawa Electric Co Ltd:The 板型ヒートパイプの製造方法
JP2000018854A (ja) * 1998-06-30 2000-01-18 Showa Alum Corp ヒートパイプ
JP2000258079A (ja) * 1999-03-04 2000-09-22 Fujikura Ltd 平板型ヒートパイプを用いた放熱構造

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61250490A (ja) * 1985-04-26 1986-11-07 スタ−リング・サ−マル・モ−タ−ズ・インコ−ポレ−テツド ヒ−トパイプ
JPH0336468A (ja) * 1989-06-30 1991-02-18 Toshiba Corp 冷却庫
JPH05203377A (ja) * 1991-11-12 1993-08-10 Mitsubishi Electric Corp 平板型ヒートパイプ及び高密度実装モジュール
JPH1062080A (ja) * 1996-08-22 1998-03-06 Mitsubishi Shindoh Co Ltd 配管部材およびヒートパイプ
JPH11201673A (ja) * 1998-01-12 1999-07-30 Furukawa Electric Co Ltd:The 板型ヒートパイプの製造方法
JP2000018854A (ja) * 1998-06-30 2000-01-18 Showa Alum Corp ヒートパイプ
JP2000258079A (ja) * 1999-03-04 2000-09-22 Fujikura Ltd 平板型ヒートパイプを用いた放熱構造

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004025198A1 (fr) * 2002-09-11 2004-03-25 Ziquan Zhao Refrigerateur polyvalent a temperature constante comportant un support thermique
US7213408B2 (en) 2002-09-11 2007-05-08 Ziquan Zhao Multifunctional constant temperature refrigerator with thermal carriers
CN102168904A (zh) * 2011-01-21 2011-08-31 上海理工大学 一种采用斯特林制冷机的酒柜
CN102168904B (zh) * 2011-01-21 2012-09-05 上海理工大学 一种采用斯特林制冷机的酒柜

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TW542892B (en) 2003-07-21

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