WO2005098336A1 - Évaporateur, thermisiphon, et chambre de refroidissement type stirling - Google Patents

Évaporateur, thermisiphon, et chambre de refroidissement type stirling Download PDF

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Publication number
WO2005098336A1
WO2005098336A1 PCT/JP2005/005525 JP2005005525W WO2005098336A1 WO 2005098336 A1 WO2005098336 A1 WO 2005098336A1 JP 2005005525 W JP2005005525 W JP 2005005525W WO 2005098336 A1 WO2005098336 A1 WO 2005098336A1
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WO
WIPO (PCT)
Prior art keywords
evaporator
refrigerant
heat exchange
pipe
heat
Prior art date
Application number
PCT/JP2005/005525
Other languages
English (en)
Japanese (ja)
Inventor
Henglang Zhang
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 WO2005098336A1 publication Critical patent/WO2005098336A1/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
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • F28D15/0266—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 with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
    • 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
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements

Definitions

  • the present invention relates to an evaporator used in a secondary refrigerant circuit, a loop thermosiphon using the evaporator, and a Stirling cooler using the loop thermosiphon.
  • the reverse Stirling refrigeration cycle employs a working gas, such as helium gas, hydrogen gas, or nitrogen gas, which does not adversely affect the global environment.
  • a Stirling refrigerator using this reverse Stirling refrigeration cycle is known as one of small refrigerators capable of generating extremely low-temperature refrigeration.
  • the Stirling refrigerator has a high-temperature section called a warm section and a low-temperature section called a cold head, depending on the shape and size of the internal heat exchange provided therein.
  • a condenser filled with a refrigerant is attached to the low-temperature portion, and an evaporator provided below the condenser ( Cooler) is connected by pipes, and natural circulation heat exchange is used.
  • a secondary refrigerant circulation circuit in which a secondary refrigerant is sealed can be exemplified.
  • a condenser attached to the low-temperature section and an evaporator disposed in the refrigerator below the condenser are connected by two refrigerant circulation pipes.
  • the secondary refrigerant circulation circuit in which the secondary refrigerant is sealed is a thermosiphon-type natural circulation circuit using a phase change of the secondary refrigerant.
  • the secondary refrigerant in the secondary refrigerant circulation circuit comes into contact with the low-temperature portion of the Stirling refrigerator and is liquefied by a condenser and flows down to the evaporator.
  • the liquid secondary refrigerant that has flowed into the evaporator undergoes heat exchange when passing through the evaporator and changes to vapor.
  • the secondary refrigerant that has turned into a vapor is a phenomenon in which the vapor rises, and the vapor turns into a liquid in the condenser. Due to the pressure difference due to the specific gravity difference when changing, and the pressure difference generated when the liquid secondary refrigerant flows down to the evaporator, the secondary refrigerant is sucked, rises and flows into the condenser. By repeating the above-described phase change and flow of the secondary refrigerant, the cold heat of the low-temperature part can be continuously conveyed into the Stirling cooler.
  • This secondary refrigerant circulation circuit utilizes natural circulation that occurs in the cooling circuit, and does not require a device such as a circulation pump for forcibly circulating the refrigerant, and thus can save energy. .
  • the evaporator has a heat exchange pipe for causing a secondary refrigerant to flow therein to exchange heat with external air.
  • a secondary refrigerant to flow therein to exchange heat with external air.
  • the cold heat of the secondary refrigerant flowing inside the heat exchange pipe is easily released to the outside.
  • cooling fins with high thermal conductivity are attached to the side of the heat exchange pipe. By attaching the fins, the air in the cooling chamber and the secondary refrigerant are cooled by the secondary refrigerant, thereby increasing the contact area (hereinafter, the heat exchange area) between the members (heat exchange pipes and cooling fins). can do.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2003-148813
  • Patent Document 2 JP-A-6-193920
  • Patent Document 3 JP 2001-33139 A
  • the heat exchange pipe has a bent or curved portion. These bends and / or bends are provided with a large number of bends and / or bends having a large flow resistance to prevent smooth flow of the refrigerant.
  • the present invention uses an evaporator in which the refrigerant flows smoothly and heat exchange between the refrigerant and the air near the evaporator is performed with high performance and high efficiency, and the evaporator is used. It is an object to provide a loop-type thermosiphon and a cooler using the loop-type thermosiphon.
  • the present invention provides an inflow port through which a liquid or substantially liquid refrigerant flows, a heat exchange pipe for evaporating the refrigerant, and an outflow port through which the refrigerant flows out.
  • the inflow port, the heat exchange pipe, and the outflow port are connected in this order, and at least a part of the heat exchange pipe has a plurality of parallel internal pipes.
  • the evaporator is provided.
  • the heat exchange pipe inside the evaporator has a plurality of parallel internal pipes, the total length of the pipe through which the refrigerant flows can be increased, and the heat exchange area increases accordingly. be able to.
  • the flow length of the refrigerant is the same or substantially the same as when the branch does not branch, the flow resistance due to the length of the pipe can be reduced, and the refrigerant flows smoothly.
  • the evaporator can increase the heat exchange area while suppressing the flow resistance of the refrigerant, so that heat can be efficiently exchanged with the air outside the evaporator (cooling the air). It comes out.
  • the inlet may be arranged below the outlet.
  • the refrigerant flows into the evaporator in a state of a liquid or a substantially liquid having a large specific gravity, evaporates in the evaporator, and flows out as a high-temperature vapor state refrigerant. Flow efficiently within the heat exchange pipe. Thereby, heat can be efficiently exchanged with the air outside the evaporator (air is cooled).
  • the heat exchange pipe may have an internal pipe branched in a vertical direction.
  • the evaporator can be formed thin.
  • the heat exchange pipe may have an internal pipe branched in a horizontal direction.
  • Examples of the use of the evaporator include, for example, those used as an evaporator of a loop-type thermosiphon. Further, an example in which the loop-type thermosiphon is used as a secondary refrigerant circulation circuit of a Stirling cooler using a Stirling refrigerator can be shown.
  • the refrigerant inside the loop-type thermosiphon can be smoothly circulated. Further, by using the loop-type thermosiphon as a secondary refrigerant circulation circuit of the Stirling refrigerator, it is possible to efficiently transfer the cold heat of the low temperature part of the Stirling refrigerator to the inside of the refrigerator.
  • One or more cooling chambers may be provided inside the Stirling cooler.
  • a cooling room such as a refrigerator room, a freezer room, a warm room, or a cool room, which cools to a temperature range in which a Stirling refrigerator can be generated, can be widely used.
  • an evaporator is used in which a refrigerant flows smoothly and heat exchange between the refrigerant and air in the vicinity of the evaporator is performed with high performance and high efficiency.
  • An object is to provide a loop-type thermosiphon and a cooler using the loop-type thermosiphon. Target.
  • FIG. 1A is an enlarged front view of the inside of an evaporator according to the present invention.
  • FIG. 1B is an enlarged view of a cooling fin provided in the cooling-side evaporator shown in FIG. 1A.
  • FIG. 2A is an enlarged plan view of the inside of an evaporator according to the present invention.
  • FIG. 2B is an enlarged front view of the evaporator shown in FIG. 2A.
  • FIG. 2C is an enlarged view of a cooling fin provided in the evaporator shown in FIGS. 2A and 2B.
  • FIG. 3 is a schematic layout diagram of a loop type thermosiphon using the evaporator shown in FIG. 1A.
  • FIG. 4 is a schematic diagram of a Stirling cooler using the loop thermosiphon shown in FIG. 3 as a secondary refrigerant circuit.
  • FIG. 1A is a sectional view of the evaporator according to the present invention
  • FIG. 1B is an enlarged view of a cooling fin of the evaporator shown in FIG. 1A.
  • the evaporator 1 shown in FIG.1A has an inlet 11 through which the refrigerant flows in, an outlet 12 through which the refrigerant flows out, and a heat exchange pipe 13 for exchanging heat between the inflowing refrigerant and external air. ing.
  • the inflow port 11, the heat exchange pipe 13, and the outflow port 12 are airtightly connected in this order.
  • the inflow port 11 is connected to a liquid refrigerant pipe 21 provided outside, through which a liquid refrigerant flows.
  • the outlet 12 is connected to a vapor refrigerant pipe 22 through which the vaporized refrigerant flows.
  • the inlet 11 is disposed below the outlet 12.
  • the heat exchange pipe 13 is connected to the inlet 11 at the upstream end, and is connected to the outlet 12 at the downstream end.
  • the heat exchange pipe 13 has a branch 131 on the upstream side, and has two parallel internal pipes 132 and 133. Further, the internal pipes 132 and 133 have a junction 134 on the downstream side, and join at the junction 134 and connect to the outlet 12.
  • the internal pipes 132 and 133 are vertically arranged in parallel. The two internal pipes 132 and 133 are folded without crossing Is returning.
  • cooling pipes are provided in the internal pipes 132 and 133 so that heat is effectively exchanged between the refrigerant flowing in the pipes and the air around the evaporator 1. 14 are installed.
  • the cooling fins 14 are not limited to this, but here, both of the internal pipings 132 and 133 pass through one cooling fin 14. By arranging the cooling fins 14 in this manner, the heat exchange area can be increased, and at the same time, the internal pipes 132 and 133 can be prevented from contacting each other, and can act as reinforcement for increasing the strength against deformation.
  • the inlet 11 Since the liquid refrigerant flowing from the inlet 11 has a higher specific gravity, the vapor refrigerant flowing out of the outlet 12 has a lower specific gravity, the inlet 11 is disposed below the outlet 12, so that the heat exchange is performed.
  • the refrigerant flows through the exchange pipe 13 smoothly. Further, inside the evaporator 1, the liquid refrigerant having a high specific gravity moves downward, and the liquid refrigerant vaporizes and the vapor refrigerant having a low specific gravity moves upward.
  • the inlet 11 into which the liquid refrigerant flows in is disposed below the outlet 12 from which the vapor refrigerant flows out, the vapor refrigerant can be prevented from flowing back through the liquid refrigerant pipe 21, and the refrigerant Can be circulated smoothly.
  • the total length of the heat exchange pipe 13 can be increased by having the two internal pipes 132 and 133 in parallel with the heat exchange pipe 13.
  • the internal pipes 132 and 133 are arranged in parallel, it is possible to suppress an increase in the length of the flow path through which the refrigerant flows.
  • the number of turns in the flow path of the refrigerant can be reduced as compared with the pipes arranged in series. Thereby, the flow resistance due to the return of the pipe can be reduced.
  • the use of the evaporator 1 has a large heat exchange area and a high heat exchange efficiency due to the long overall length of the heat exchange pipe 13, and has a low flow resistance in the refrigerant flow path. It can flow smoothly and efficiently exchange heat with the air around the evaporator 1 (cool the surrounding air). Further, the evaporator 1 of the present embodiment branches the internal pipes 132 and 133 in the vertical direction, so that the thickness in the width direction can be suppressed. As a result, it is possible to provide a compact evaporator 1 without reducing the heat exchange capacity.
  • At least one of the branching portion 131 and the merging portion 134 may be formed so as to reduce flow resistance. As a result, the refrigerant can flow smoothly, and the heat exchange effect of the evaporator 1 can be improved. Rate can be increased. Also,
  • FIG. 2A is an enlarged plan view of the internal shape of the cooling-side evaporator of the Stirling refrigerator according to the present invention
  • FIG. 2B is an enlarged front view of the internal shape of the cooling-side evaporator shown in FIG. 2A
  • FIG. FIG. 2B is an enlarged view of a cooling fin of the cooling-side evaporator shown in FIGS. 2A and 2B.
  • the evaporator 3 shown in Figs. 2A, 2B, and 2C is one in which the heat exchange pipe 33 is branched in the horizontal direction.
  • the other parts are the same as those of the evaporator 1 shown in FIG. 1, and the substantially same parts are denoted by the same reference numerals.
  • the heat exchange pipe 33 is connected to the inlet 31 at the upstream end, and is connected to the outlet 32 at the downstream end.
  • the heat exchange pipe 33 has a branch portion 331 on the upstream side, and has two parallel internal pipes 332 and 333. Further, the internal pipes 332 and 333 have a junction 334 on the downstream side, and join at the junction 334 and connect to the outlet 32.
  • the entire length of the heat exchange pipe 33 through which the refrigerant flows increases, that is, the heat exchange area increases.
  • the internal pipes 332 and 333 are arranged in parallel, it is possible to suppress an increase in the length of the flow path through which the refrigerant flows.
  • the number of times the refrigerant is turned back in the flow path of the refrigerant can be reduced as compared with the pipes arranged in series. Thereby, the flow resistance due to the return of the pipe can be reduced.
  • the internal pipes 332 and 333 are provided with cooling fins so that heat can be exchanged effectively between the refrigerant flowing in the pipes and the air around the evaporator 3. 34 are attached.
  • the cooling fins 34 are not limited to this, but here, both the internal pipes 332 and 333 pass through one cooling fin 34 (see FIG. 2C). By arranging the cooling fins 34 in this manner, the heat exchange area can be increased, and at the same time, the internal pipes 332, 333 can be prevented from contacting each other, and can act as reinforcement for increasing the strength against deformation.
  • the evaporator 3 has a large heat exchange area and a high heat exchange capacity due to the long overall length of the heat exchange pipe 33, and the refrigerant flows smoothly because the flow resistance in the refrigerant flow path is small. It is possible to efficiently exchange heat with the air around the evaporator 3 (cool the surrounding air). Since the internal pipes 332 and 333 are branched in the horizontal direction, the height in the vertical direction can be suppressed. As a result, compactness without reducing heat exchange capacity It is possible to provide an efficient evaporator 3.
  • the number of force branching lines exemplifying a case where the internal pipe is branched into two pipes is not limited to two, and may be further branched.
  • the internal pipe of the cooling-side evaporator is branched in the up-down direction and the left-right direction, for example, but is not limited thereto, but may be branched in both the up-down and left-right directions.
  • FIG. 3 shows a schematic layout diagram of a loop-type thermosiphon using the evaporator shown in FIG. 1A.
  • the loop-type thermosiphon 4 has an evaporator 1, a condenser 5, a liquid refrigerant pipe 21, and a vapor refrigerant pipe 22.
  • the condenser 5 is arranged above the evaporator 1.
  • a liquid refrigerant pipe 21 and a vapor refrigerant pipe 22 are hermetically connected to the condenser 5.
  • the evaporator 1 has an inlet 11 connected to a liquid refrigerant pipe 21 and an outlet 12 connected to a vapor refrigerant pipe 22.
  • the inside of the loop type thermosiphon 4 is filled with a refrigerant.
  • a cooling device for example, a cooling fan not shown is provided outside the condenser 5 to cool the refrigerant inside the condenser 5.
  • the refrigerant cooled by the condenser 5 flows down through the liquid refrigerant pipe 21 and flows into the inlet 11 of the evaporator 1.
  • the liquid refrigerant flowing into the inlet 11 of the evaporator 1 flows inside the heat exchange pipe 13.
  • the liquid refrigerant flows into the internal pipes 132 and 133 at the branch portion 131 and flows.
  • the liquid refrigerant flowing through the internal pipes 132 and 133 exchanges heat with the air outside the evaporator 1 (the air is cooled) and is heated and evaporated.
  • the evaporated refrigerant merges at the junction 134 and flows into the vapor refrigerant pipe 22 from the outlet 12.
  • the vapor refrigerant rises in the vapor refrigerant pipe 22 and flows into the condenser 5 due to the power of the high-temperature vapor rising and the pressure fluctuation due to the change in specific gravity when changing from gas to liquid in the condenser 5.
  • the refrigerant can be circulated inside the loop type thermosiphon 4 without using a forced circulation device such as a pump.
  • the heat exchange pipe 13 has two parallel internal pipes 132 and 133, the total length of the pipes through which the refrigerant flows can be lengthened. By being in parallel, pressure loss can be kept low, and heat exchange with the outside air can be performed efficiently.
  • FIG. 4 shows a schematic diagram of a stirling cooler using the loop type thermosiphon shown in FIG. 3 as a secondary refrigerant circulation circuit.
  • the Stirling cooler A shown in FIG. Loop type thermosiphon 4 (secondary refrigerant circulation circuit) that conveys the cold generated by one ring refrigerator 7 and Stirling refrigerator 7 to the inside of the refrigerator, and transports the heat generated by Stirling refrigerator 7 to the outside of the refrigerator.
  • the heat radiation side natural circulation circuit 8 is provided.
  • the main body 6 has a cooling chamber 61 for accumulating cold heat therein to cool articles, and a machine chamber 62 for disposing the Stirling refrigerator 7 therein.
  • the machine room 62 is arranged above the cooling room 61, and the cooling room 61 and the machine room 62 are separated by a heat insulating wall 63.
  • the Stirling refrigerator 7 is mounted on a heat insulating wall 63 via a buffer member 631. This prevents the vibration generated in the starling refrigerator 7 from being transmitted to the heat insulating wall 63.
  • the Stirling refrigerator 7 has a low-temperature section 71 that generates cold heat and a high-temperature section 72 that generates warm heat.
  • the low-temperature section 71 has the loop-type thermosiphon 4 attached thereto, and the high-temperature section 72 has the radiation-side natural circulation circuit 8 attached thereto.
  • Secondary refrigerant circulation circuit 4 includes condenser 5 connected to low-temperature section 71, evaporator 1 provided in cooling chamber 61, liquid refrigerant pipe 21, and vapor refrigerant pipe 22. ing. Connection of the condenser 5, the evaporator 1, the liquid refrigerant pipe 21 and the vapor refrigerant pipe 22 is the same as that of the loop type thermosiphon shown in FIG. That is, the liquid refrigerant pipe 21 and the vapor refrigerant pipe 22 are airtightly connected to the condenser 5. Further, the liquid refrigerant pipe 21 and the inflow port 11 of the evaporator 1 are airtightly connected. Further, the vapor refrigerant pipe 21 and the outlet 12 of the evaporator 1 are airtightly connected. The loop type thermosiphon 4 is formed by filling the secondary refrigerant.
  • the secondary refrigerant in the condenser 5 is cooled and liquefied by the cold heat of the low-temperature section 71.
  • the liquefied secondary refrigerant flows down the liquid refrigerant pipe 21 and flows into the inlet 11 of the evaporator 1.
  • the liquid secondary refrigerant that has flowed into the evaporator 1 absorbs heat from the air inside the cooling chamber 61 (cools the internal air) inside the evaporator 1 and is heated and evaporated.
  • the evaporated secondary refrigerant flows into the vapor refrigerant pipe 22 from the outlet 12.
  • the vapor refrigerant rises in the vapor refrigerant pipe 22 and flows into the condenser 5 due to a phenomenon in which the high-temperature vapor rises and a pressure change due to a change in specific gravity when the refrigerant changes from a gas to a liquid in the condenser 5.
  • the secondary refrigerant circulates inside the loop type thermosiphon 4 without using a forced circulation device such as a pump.
  • the natural circulation circuit 8 on the heat radiation side is arranged such that the evaporator 81 on the heat radiation side contacts the high temperature part 72 of the Stirling refrigerator 7 and is A hot side condenser 82 is arranged.
  • the heat radiation side evaporator 81 and the heat radiation side condenser 82 are connected by a heat radiation circuit 83 to form a natural circulation circuit.
  • the heat radiation side natural circulation circuit 8 is not limited to this, but here, water is used as the refrigerant.
  • a blower fan 84 for sending air to the heat radiation side condenser 82 is disposed close to the heat radiation side condenser 82.
  • the heat radiation side evaporator 81 takes heat from the high temperature part 72 of the Stirling refrigerator 7, and evaporates the refrigerant inside the heat radiation side evaporator 81.
  • the evaporated refrigerant rises inside the heat radiation circuit 83 and is sent to the condenser 82 on the heat radiation side.
  • the phase changes to liquid by passing heat to the radiating side evaporator 81 of the radiating circuit 83.
  • the cooling chamber has a force exemplified by one provided inside the Stirling cooler.
  • a plurality of cooling chambers may be provided instead of the one limited thereto.
  • it is possible to widely use a cooling room such as a refrigerator room, a freezer room, a warm room, a cool room, etc., which cools to a temperature range in which a Stirling refrigerator can be generated.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

Un évaporateur est formé avec une ouverture d’admission par laquelle pénètre un liquide ou un agent frigorigène substantiellement liquide, une tuyauterie d’échange de chaleur pour faire évaporer l’agent frigorigène, et une ouverture d’écoulement à partir de laquelle s’écoule l’agent frigorigène. L’ouverture d’entrée, la tuyauterie d’échange de chaleur et l’ouverture d’écoulement sont reliées dans cet ordre, et au moins une partie de la tuyauterie d’échange de chaleur est déviée vers des tuyaux internes parallèles.
PCT/JP2005/005525 2004-03-30 2005-03-25 Évaporateur, thermisiphon, et chambre de refroidissement type stirling WO2005098336A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004-100294 2004-03-30
JP2004100294A JP2005283022A (ja) 2004-03-30 2004-03-30 蒸発器、サーモサイフォン及びスターリング冷却庫

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WO2005098336A1 true WO2005098336A1 (fr) 2005-10-20

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5405015B2 (ja) 2007-12-19 2014-02-05 ホシザキ電機株式会社 冷却装置
JP6095554B2 (ja) * 2013-11-20 2017-03-15 好史 大良 放熱パイプ
KR101871369B1 (ko) * 2016-07-08 2018-06-26 남재일 열대 기후에 적합한 빌트인용 고효율 에어워터 시스템

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09138033A (ja) * 1995-11-16 1997-05-27 Furukawa Electric Co Ltd:The 空調用熱交換器及び空調システム
JP2003050073A (ja) * 2001-08-03 2003-02-21 Sharp Corp スターリング冷凍システム及びスターリング冷蔵庫

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09138033A (ja) * 1995-11-16 1997-05-27 Furukawa Electric Co Ltd:The 空調用熱交換器及び空調システム
JP2003050073A (ja) * 2001-08-03 2003-02-21 Sharp Corp スターリング冷凍システム及びスターリング冷蔵庫

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