WO2003085345A1 - Thermosiphon du type a boucle et refrigerateur a cycle de stirling - Google Patents

Thermosiphon du type a boucle et refrigerateur a cycle de stirling Download PDF

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Publication number
WO2003085345A1
WO2003085345A1 PCT/JP2003/004399 JP0304399W WO03085345A1 WO 2003085345 A1 WO2003085345 A1 WO 2003085345A1 JP 0304399 W JP0304399 W JP 0304399W WO 03085345 A1 WO03085345 A1 WO 03085345A1
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WO
WIPO (PCT)
Prior art keywords
evaporator
working fluid
loop
condenser
heat
Prior art date
Application number
PCT/JP2003/004399
Other languages
English (en)
Japanese (ja)
Inventor
Hengliang Zhang
Wei Chen
Masaaki Masuda
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
Priority to AU2003236294A priority Critical patent/AU2003236294A1/en
Priority to CA2481477A priority patent/CA2481477C/fr
Priority to EP03745945A priority patent/EP1493983A4/fr
Priority to US10/510,502 priority patent/US20050172644A1/en
Priority to KR1020047015931A priority patent/KR100691578B1/ko
Priority to BR0309143-0A priority patent/BR0309143A/pt
Publication of WO2003085345A1 publication Critical patent/WO2003085345A1/fr

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Classifications

    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
    • F25B23/006—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect boiling cooling systems
    • 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
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • 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
    • 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

Definitions

  • the present invention relates to a 'loop-type thermosiphon and a Stirling refrigerator using the loop-type thermosiphon. Background art,.
  • Heat sinks, heat pipes, thermosiphons, etc. are used to cool heating equipment and electronic cooling elements. Since the heat sink has a temperature distribution in the base of the heat sink to which the heat source is attached, the further away from the heat source, the less the heat contributes to heat dissipation. Heat pipes or thermosiphons are characterized by high heat transfer capacity and small temperature changes even when heat is transferred to a location far from the heat source.
  • the number of heat pipes required increases as the amount of heat transfer increases because the flow of the working fluid vapor and the liquid flow in the same pipe.
  • the heat transfer will be 10 O WS.
  • the heat transfer coefficient of the air is low.
  • a tubular thermosiphon that returns the liquid to the evaporator by gravity has the same characteristics.
  • the loop-type thermosiphon also has a structure in which the liquid condensed in the condenser by gravity returns to the evaporator.
  • the shape and size of the condenser can be designed not only according to the cooling means of the condenser, but also the evaporator can be designed according to the shape and size of the heat source. Therefore, in most cases, only two pipes, a gas pipe and a liquid pipe, connecting the condenser and the evaporator can be used. Of course, the condenser must be located higher than the evaporator.
  • the loop-type thermosiphon has a problem that the circulation flow rate is difficult to stabilize depending on the type of working fluid to be enclosed or when the heat load fluctuates within a certain range. Temperature fluctuates frequently.
  • CFC specified chlorofluorocarbon
  • HCFC-based refrigerants have been used as working fluids and secondary working fluids for cooling equipment, but CFC-based refrigerants have already been completely abolished, and HCFC-based refrigerants are also in the ozone layer. Regulated by international conventions of protection.
  • HFC-based refrigerants do not destroy the ozone layer, but are powerful warming substances with a global warming potential of several hundred to several thousand times that of carbon dioxide, and are subject to emission regulations. . Therefore, the type of refrigerant that can be selected from the viewpoint of environmental protection is also limited as the working fluid of the loop-type thermosiphon.
  • natural refrigerants that are environmentally friendly include media such as HC-based refrigerants, ammonia, carbon dioxide, water, and ethanol, and mixtures thereof.
  • the conventional loop-type thermosiphon consists of an evaporator 101 and a condenser, as shown in Fig. 5.
  • Heat source 105 is cooled in evaporator 101.
  • the condenser 103 is provided at a position higher than the evaporator 101, and the working fluid liquefied in the condenser 103 is vaporized in a gas-liquid separation tank 106 provided between the condenser and the evaporator. The liquid is separated. The liquid of the working fluid passes through the pipe 104 by gravity and is introduced into the evaporator from the lower part of the evaporator 101.
  • the working fluid that has taken heat from the heat source is vaporized in the evaporator 101, and the steam of the working fluid is passed through the pipe 102 due to the steam pressure difference between the evaporator and the condenser, and the condenser 1 Introduced at 03.
  • the evaporator 101 is designed according to the shape of the heat source.
  • the gas-liquid separation tank I ⁇ 6 is not always necessary.
  • Japanese Patent Application Laid-Open No. H11-122304 discloses a method for cooling a warm part of a Stirling refrigerator by using a liquid of a secondary refrigerant using a pump.
  • the conventional loop-type thermosiphon has a drawback that the circulation flow rate of the working fluid tends to be unstable, which causes the temperature of the heat source to fluctuate.
  • the temperature of the heat source often fluctuates drastically. If the temperature of the heat source fluctuates drastically, not only the performance of the heat source device becomes unstable, but also the heat source device may be damaged.
  • a loop-type thermosiphon is used, for example, for cooling a high-temperature portion of a Stirling refrigerator and the Stirling refrigerator is mounted in a refrigerator.
  • the heat load of refrigerators varies from season to season.
  • the heat load of the refrigerator fluctuates Also, the amount of heat radiation in the high temperature part of the Stirling refrigerator changes.
  • Loop type thermosiphons often exhibit unstable operation with fluctuating heat loads. In such a case, if the temperature of the high temperature part of the Stirling refrigerator fluctuates drastically, it is not enough that the COP (Coefficient of Performance) of the Stirling refrigerator fluctuates only. If the temperature of the high temperature part is too high, the regenerator of the Stirling refrigerator may be broken.
  • Fig. 6 shows a conventional loop-type thermosiphon evaporator that cools a cylindrical heat source.
  • This evaporator 101 has an annular shape to cool the cylindrical heat source 105, and the cylindrical heat source 105 is fitted into the hole of the evaporator and closely adheres to the surface of the hole of the evaporator. are doing.
  • An internal fin (not shown) is provided on the surface of the hole of the evaporator to increase the evaporation area.
  • the liquid from the condenser flows from the lower part of the evaporator through the pipe 104 to the liquid pool 1 211, and the vaporized vapor flows out of the upper part of the evaporator through the pipe 102 to the condenser. .
  • Figure 7 shows the change in the heat source temperature during the experimental operation of the loop-type thermosiphon using the evaporator and piping structure shown in Fig. 6 and filled with water as the working fluid.
  • the heat value of the heat source falls below 75% of the design load, the temperature of the heat source fluctuates as shown in Fig. 7. No improvement was observed even when the amount of working fluid was changed.
  • An object of the present invention is to provide a loop-type thermosiphon that can stably maintain the temperature of a high-temperature heat source even if the fluctuation of the heat load is large, and a Stirling refrigerator equipped with the loop-type thermosiphon.
  • the loop-type thermosiphon of the present invention is a loop-type thermosiphon that uses a working fluid to transfer heat from a high-temperature heat source.
  • the loop-type thermosiphon has a heat absorbing section, an evaporator that removes heat from the high-temperature heat source through the heat absorbing section to evaporate the working fluid, and that is located at a position higher than the high-temperature heat source and evaporates by the evaporator.
  • a condenser for condensing the working fluid and a pipe connecting the evaporator and the condenser so as to form a loop. Then, the working fluid that has passed through the condenser is brought into contact with the heat absorbing section before the working fluid accumulates in the liquid pool of the working fluid in the evaporator. .
  • FIG. 1 is a basic configuration diagram of a loop-type thermosiphon according to Embodiment 1 of the present invention.
  • FIG. 2 is a diagram showing a modification of the loop-type thermosiphon according to the first embodiment of the present invention. .
  • FIG. 3 is a diagram showing a Stirling refrigerator according to Embodiment 2 of the present invention.
  • FIG. 4 is a diagram showing the stability of the heat source temperature when the loop thermosiphon according to Embodiment 3 of the present invention is used.
  • FIG. 5 is a diagram showing a configuration of a general loop-type thermosiphon.
  • FIG. 6 is a diagram showing a conventional loop-type thermosiphon evaporator.
  • FIG. 7 is a diagram showing a change in heat source temperature when a conventional loop-type thermosiphon is used. '' Best mode for carrying out the invention
  • FIG. 1 is a conceptual diagram illustrating a basic configuration of a loop-type thermosiphon according to Embodiment 1 of the present invention.
  • the loop-type thermosiphon shown in Fig. 1 has an evaporator 1, a condenser 3, a gas pipe 2 that is a pipe from the evaporator 1 to the condenser 3, and a liquid pipe 4 that is a pipe from the condenser 3 to the evaporator 1. It is composed of
  • the high-temperature heat source 5 to be cooled has a cylindrical heat radiation surface
  • the generator has an annular shape provided with a round hole of the same size corresponding to the cylindrical heat radiation surface of the heat source.
  • the condenser 3 is a fin-tube type, in which a working fluid flows inside the pipe, and outside the pipe, air flows to cool the working fluid.
  • the working fluid pipe of the condenser can be parallel flow type (Parallel Flow) type or Serpentine type.
  • the condenser is installed with the gas inlet higher than the condensed liquid outlet.
  • the gas pipe 2 from the evaporator 1 to the condenser 3 uses a thicker pipe than the liquid pipe 4 from the condenser to the evaporator. For this reason, the flow resistance of the gas pipe 2 is made smaller than the flow resistance of the liquid pipe 4. This is to prevent backflow of the working fluid and difficulty in starting.
  • the diameter of the liquid pipe was determined based on the design heat load and the thermophysical properties of the working fluid. In order to form a thermosiphon, the condenser 3 is positioned higher than the evaporator 1.
  • pure water is sealed as a working fluid.
  • Fill the liquid with 13 to 2 Z3, which is the total volume of liquid that can be stored in the condenser (for example, the header pipe at the condenser outlet), the volume of the liquid pipe, and the volume of the evaporator.
  • the remaining volume is filled with the saturated steam of the working fluid at the working temperature, and the mass of the working fluid is defined as the sealed volume.
  • the operation of the working fluid can be made smooth by this amount of sealing.
  • water takes heat from the high-temperature heat source 5 in the evaporator 1 and evaporates.
  • the steam evaporated in the evaporator 1 flows into the condenser 3 through the gas pipe 2 by utilizing the difference in steam pressure due to the temperature difference between the condenser 3 and the evaporator 1, and transfers heat to the air outside the pipe. It is deprived and condensed.
  • the liquid condensed in the condenser 3 returns to the evaporator 1 again through the liquid pipe 4 by gravity. In this way, the process in which the working fluid circulates, absorbs heat in the evaporator, and releases heat in the condenser is repeated.
  • the liquid from the condenser is introduced from the upper part of the evaporator as shown in FIG. 1, instead of being introduced from the lower part of the evaporator (see FIG. 5). It is here.
  • cold liquid is supplied to the lower part of the evaporator. For this reason, the influence of the temperature gradient in the liquid stored in the evaporator on the flow is small, and the evaporation is not promoted.
  • the loop-type thermosiphon according to the present embodiment shown in FIG. 1 is configured such that the liquid from the condenser is introduced from the upper part of the evaporator so that the liquid having a supercooling degree is first heated to a high-temperature heat absorbing portion or an internal portion (not shown). Preheated by falling into fins. The inner fin is attached to the heat absorbing part and is formed toward the inside of the evaporator. 'This makes it easier for the liquid stored in the evaporator to evaporate.
  • the cooler liquid enters from above the liquid level in the evaporator and tries to move downward by the force of gravity due to the difference in density, the liquid in the evaporator is stirred and the evaporation is promoted. Bubbles adhering to the heat transfer surface will peel off and break easily.
  • the loop-type thermosiphon according to the present embodiment can obtain a stable heat source temperature even under conditions away from the designed heat load.
  • the loop-type thermosiphon shown in FIG. 1 does not have a gas-liquid separation tank.
  • a gas-liquid separation tank 6 may be provided between the condenser and the evaporator as shown in FIG. However, when determining the amount to be filled, the internal volume of the gas-liquid separation tank should be considered as a part of the liquid pipe. Providing a gas-liquid separation tank may be effective for the stable operation of a loop-type thermosiphon. By adding 60 ° / 0 or less ethanol to the working fluid, the permissible ambient temperature for operation and transportation can be reduced.
  • FIG. 3 is a conceptual diagram of a staring refrigerator according to Embodiment 2 of the present invention equipped with a loop-type thermosiphon.
  • the Stirling refrigerator shown in Fig. 3 has a Stirling refrigerator, a loop-type thermosiphon attached to the cooling of the high-temperature part of the Stirling refrigerator, and the cold heat of the low-temperature part of the Stirling refrigerator, which is installed in the refrigerator main body 19. It consists of a side heat exchange system and a refrigerator body.
  • the low-temperature side heat exchange system is also a loop-type thermosiphon, but is a loop-type thermosiphon not covered by the present embodiment.
  • a Stirling refrigerator 11 having a columnar high temperature part and a low temperature part is arranged on the back of the refrigerator.
  • a loop-type thermosiphon that cools the high-temperature section 13 of the Stirling refrigerator Attach the generator 1 to the high-temperature part of the Stirling refrigerator and bring it into close contact.
  • the condenser '3 is placed on the refrigerator body, and the evaporator 1 and the condenser 3 are connected by a pipe as shown in Fig. 1, so that the loop-type thermosiphon according to the present embodiment can be used in the Stirling refrigerator.
  • the skin tube 4 is inserted into the evaporator 1 from above.
  • the working fluid is filled with pure water or a mixture of pure water and ethanol.
  • Refrigerator cooler 15 is installed inside the cool air duct.
  • the temperature of the high temperature part 13 of the Stirling refrigerator rises, the working fluid is heated by the evaporator 1 and evaporates, and flows into the condenser 3 through the gas pipe 2.
  • the air outside the refrigerator is introduced by the rotation of the fan 7, and the working fluid gas from the evaporator 1 is cooled by the condenser 3 and condensed.
  • the working fluid liquefied in the condenser 3 returns to the evaporator 1 by gravity through the liquid pipe 4 and the inlet pipe 4a.
  • the liquefied working fluid returns to the evaporator 1, it contacts the heat absorbing portion 1a of the evaporator and / or the internal fin (not shown) to exchange heat.
  • the natural circulation of the working fluid is performed, and the heat of the Stirling refrigerator 11 is transmitted to the air outside the refrigerator.
  • the operation of the Stirling refrigerator 11 lowers the temperature of the low temperature section 12 and the secondary refrigerant of the heat exchange system flowing through this low temperature section loses heat.
  • the secondary refrigerant of this low-temperature side heat exchange system absorbs heat from the air in the refrigerator by the rotation of the cooling fan 16 in the refrigerator cooler. Above the cooling fan, a damper 17 is arranged.
  • the secondary refrigerant of the low-temperature side heat exchange system naturally circulates by gravity.
  • a circulation means using a pump may be used.
  • the cold heat of the Stirling refrigerators 1 and 1 is continuously provided to the air in the refrigerator.
  • drain water formed by defrosting the refrigerator cooler 15 is discharged from the drain water outlet 18.
  • FIG. 4 is a diagram showing temperature fluctuations of a high-temperature heat source when the loop-type thermosiphon according to Embodiment 3 of the present invention is used.
  • the loop-type thermosyphon according to the present embodiment is configured to return the liquid to the evaporator in the conventional loop-type thermosiphon shown in FIG. It is a device that simply changes the way it is connected. That is, the condensed working fluid is not directly introduced into the liquid pool, but is returned so as to come into contact with the heat absorbing portion that is not in contact with the liquid pool.
  • the time lapse of the high-temperature heat source temperature shown in Fig. 4 is the effect obtained under the same heat load conditions as the conventional loop-type thermosiphon. Compared to the large temperature fluctuation of the heat source in the conventional loop-type thermosiphon shown in Fig. 7, a stable temperature transition can be obtained.
  • a loop-type thermosiphon for transferring heat from a high-temperature heat source having a heat-radiating surface, comprising: an evaporator for removing heat from the high-temperature heat source; a condenser disposed above the heat source; A pipe connecting the evaporator and the condenser is provided to form the air, the working fluid is sealed, and when the working fluid liquid from the condenser is introduced into the evaporator, it is dropped on the heat absorbing part to exchange heat.
  • an internal fin is provided in a heat absorbing portion in an evaporator constituting the loop-type thermosiphon, and a liquid of a working fluid condensed in the condenser is supplied to the evaporator. It is introduced into the evaporator so as to fall from the upper part into the heat absorbing portion and the internal fins in the evaporator.
  • the evaporator may have a box shape, or may have a semi-circular shape in combination to form a ring. Further, other shapes may be combined.
  • the heat absorbing section may be formed in a cylindrical shape or a hole so as to receive a high-temperature heat source.
  • the working fluid can be preheated by utilizing the heat from the upper half of the cylindrical heat-dissipating surface of the high-temperature heat source, which does not emit as much heat as the lower half inside the evaporator. And the temperature of the high-temperature heat source can be stabilized.
  • the flow resistance of the gas pipe for guiding the vapor evaporated by the evaporator to the condenser is determined by the flow of the liquid pipe for guiding the liquid condensed by the condenser to the evaporator. Make it smaller than resistance. With this configuration, it is possible to prevent the backflow of the working fluid and the difficulty in starting the working fluid seen in the thermosiphon.
  • the flow resistance of the pipe is reduced if the transfer heat is large, and the flow resistance of the liquid pipe is reduced if the transfer heat is small. It is better to increase the flow resistance.
  • a more stable circulating flow rate of the working fluid can be obtained.
  • a reference value of the amount of heat transferred for example, a design load of 75 ° / ⁇ can be used. In other words, when the heat value of the heat source is 75% or less of the design load, the flow resistance of the above piping is increased, and when it exceeds 75%, the flow resistance of the above piping is reduced.
  • Other reference values for example, a value such as 50% of the design load, may be used.
  • the amount of the working fluid to be filled is 1 mm of the volume capable of storing the liquid in the condenser at the operating temperature, the volume of the liquid pipe (pipe), and the volume of the evaporator. It is possible to fill 3 to 2 33 with liquid and fill the remaining volume with the saturated steam of the working fluid at the working temperature and fill the mass of the working fluid. With this configuration, problems caused by the amount of working fluid enclosed can be eliminated.
  • the loop-type thermosiphon uses a natural refrigerant such as carbon dioxide gas, water, or hydrated carbon as a working fluid, and can provide an environmentally friendly heat exchange technique.
  • a natural refrigerant such as carbon dioxide gas, water, or hydrated carbon
  • water as the working fluid
  • a highly safe loop-type thermosiphon with no toxicity or flammability can be obtained.
  • the evaporator of the loop-type thermosiphon exchanges heat with a high-temperature portion of the Stirling refrigerator.
  • both can be brought into close contact with each other, and the condenser can be placed at a higher temperature than the high temperature part of the stirling refrigerator of the refrigerator.
  • loop thermosiphon of the broadest embodiment of the present invention does not need to have the effects of the above embodiments. Good.
  • Loop type thermosa of the widest embodiment of the present invention The microphone need only have an effect of operating stably in response to the load fluctuation of the heat source.
  • the loop-type thermosiphon by this effort can absorb the fluctuation of the heat load of the heat source and operate stably.
  • the above-mentioned loop-type thermosiphon is used to cool the high-temperature part of a Stirling refrigerator, for example, in refrigerators that use a Stirling refrigerator that does not use Freon and emits no warming gas, as a cooling device. It is expected to contribute to secure stable refrigeration performance.

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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)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

L'invention concerne un thermosiphon du type à boucle capable de fonctionner de manière stable, indépendamment de la fluctuation de la charge thermique, et un réfrigérateur à cycle de Stirling équipé de ce thermosiphon, dans lequel la chaleur est véhiculée au moyen d'un fluide de travail depuis une source de chaleur haute température (5). Le thermosiphon comporte une unité d'absorption (1a), un évaporateur (1) qui extrait la chaleur de la source susmentionnée, via l'unité d'absorption, et qui évapore le fluide de travail, un condenseur (3) dont la position est plus élevée que celle de la source de chaleur, et qui condense le fluide de travail évaporé dans l'évaporateur, et enfin des conduites (2, 4) d'interconnexion entre l'évaporateur et le condenseur, selon une configuration de boucle. Le fluide de travail (22) qui traverse le condenseur (3) est mis en contact avec l'unité d'absorption (1a), avant le stockage du fluide dans un contenant pour liquide (21), ce qui permet l'échange thermique.
PCT/JP2003/004399 2002-04-08 2003-04-07 Thermosiphon du type a boucle et refrigerateur a cycle de stirling WO2003085345A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
AU2003236294A AU2003236294A1 (en) 2002-04-08 2003-04-07 Loop-type thermosiphon and stirling refrigerator
CA2481477A CA2481477C (fr) 2002-04-08 2003-04-07 Thermosiphon du type a boucle et refrigerateur a cycle de stirling
EP03745945A EP1493983A4 (fr) 2002-04-08 2003-04-07 Thermosiphon du type a boucle et refrigerateur a cycle de stirling
US10/510,502 US20050172644A1 (en) 2002-04-08 2003-04-07 Loop-type thermosiphon and stirling refrigerator
KR1020047015931A KR100691578B1 (ko) 2002-04-08 2003-04-07 루프형 열사이펀
BR0309143-0A BR0309143A (pt) 2002-04-08 2003-04-07 Termossifão do tipo de laço e refrigerador stirling

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002104896A JP4033699B2 (ja) 2002-04-08 2002-04-08 ループ型サーモサイホンおよびスターリング冷蔵庫
JP2002-104896 2002-04-08

Publications (1)

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WO2003085345A1 true WO2003085345A1 (fr) 2003-10-16

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PCT/JP2003/004399 WO2003085345A1 (fr) 2002-04-08 2003-04-07 Thermosiphon du type a boucle et refrigerateur a cycle de stirling

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US (1) US20050172644A1 (fr)
EP (1) EP1493983A4 (fr)
JP (1) JP4033699B2 (fr)
KR (1) KR100691578B1 (fr)
CN (1) CN100350211C (fr)
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BR (1) BR0309143A (fr)
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CN1646871A (zh) 2005-07-27
CA2481477A1 (fr) 2003-10-16
AU2003236294A1 (en) 2003-10-20
CN100350211C (zh) 2007-11-21
CA2481477C (fr) 2011-12-20
US20050172644A1 (en) 2005-08-11
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JP4033699B2 (ja) 2008-01-16
KR100691578B1 (ko) 2007-03-12

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