US20070028626A1 - Loop type thermo siphon, stirling cooling chamber, and cooling apparatus - Google Patents

Loop type thermo siphon, stirling cooling chamber, and cooling apparatus Download PDF

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Publication number
US20070028626A1
US20070028626A1 US10/570,132 US57013206A US2007028626A1 US 20070028626 A1 US20070028626 A1 US 20070028626A1 US 57013206 A US57013206 A US 57013206A US 2007028626 A1 US2007028626 A1 US 2007028626A1
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Prior art keywords
pipe
condenser
working fluid
evaporator
pipes
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US10/570,132
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English (en)
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Wei Chen
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Sharp Corp
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Sharp Corp
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Priority claimed from JP2003309708A external-priority patent/JP2005077018A/ja
Priority claimed from JP2004020679A external-priority patent/JP3689761B2/ja
Application filed by Sharp Corp filed Critical Sharp Corp
Assigned to SHARP KABUSHIKI KAISHA reassignment SHARP KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHEN, WEI
Publication of US20070028626A1 publication Critical patent/US20070028626A1/en
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    • 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
    • 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
    • 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
    • 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
    • F28D1/04—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 tubular conduits
    • F28D1/047—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 tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
    • F25D2317/0682—Two or more fans
    • 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
    • F28D2015/0216—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 having particular orientation, e.g. slanted, or being orientation-independent

Definitions

  • the present invention relates generally to loop thermosyphons, Stirling refrigerators having the loop thermosyphon mounted, and cooling apparatuses equipped with a Stirling refrigerating machine.
  • heat radiation systems employing heat sinks, heat pipes, thermosyphons and the like have been known as heat radiation systems radiating heat generated from heat sources.
  • the heat sink For a heat radiation system with a heat sink attached to a heat source, the heat sink has a significant distribution in temperature. As such, the remoter it is from the heat source, the less it contributes to heat radiation. It thus has its limit in improving heat radiation performance.
  • heat radiation systems employing a heat pipe, a thermosyphon or the like employ a working fluid to transfer heat generated at a heat source. As such, they have a significantly higher ability to transfer heat than a heat sink and can thus maintain high heat radiation performance.
  • thermosyphon is a gravity driven heat transfer device utilizing a difference in density of a working fluid that is caused as the working fluid evaporates and condenses.
  • a loop thermosyphon is a thermosyphon configured to circulate a working fluid in a closed circuit formed in a loop.
  • FIGS. 17A and 17B schematically show the first conventional example of loop thermosyphon in structure, as seen in front and side views, respectively.
  • a loop thermosyphon 100 I includes an evaporator 110 depriving a heat source of heat and a condenser 130 I externally discharging heat.
  • Evaporator 110 and condenser 130 I are connected by a feed pipe 120 and a return pipe 140 , and evaporator 110 , feed pipe 120 , condenser 130 I and return pipe 140 together form a closed circuit.
  • condenser 130 I is disposed at a position higher than evaporator 110 .
  • evaporator 110 a working fluid deprives the heat source of heat and thus evaporates, and ascends by a vapor pressure difference between evaporator 110 and condenser 130 I against gravity through feed pipe 120 and enters condenser 130 I.
  • Condenser 130 I cools and thus condenses the working fluid, which is in turn pulled by gravity, and thus descends through return pipe 140 and enters evaporator 110 .
  • Such convection of the working fluid involving a change in phase as described above allows the heat source to externally radiate heat.
  • FIG. 20 is a side view schematically showing a configuration of the cooling apparatus in the second conventional example.
  • the figure shows a cooling apparatus 50 including a heat transfer cycle 5 associated with a cold portion and extracting cold generated at Stirling refrigerating machine 1 , and a heat transfer cycle 4 associated with a heated portion and externally radiating hot.
  • Stirling refrigerating machine 1 includes a cold portion 3 absorbing heat to generate cold as an internally sealed working medium (e.g., helium) expands, and a heated portion 2 generating hot as the working medium expands.
  • an internally sealed working medium e.g., helium
  • Heat transfer cycle 5 associated with the cold portion is generally a circulation circuit including a condenser 12 associated with the cold portion and attached around and in contact with cold portion 3 , and an evaporator 15 associated with the cold portion and connected to condenser 12 via a condensate coolant pipe 13 and a vapor coolant pipe 14 .
  • This circuit has carbon dioxide, hydrocarbon or the like sealed therein as a coolant to form a thermosyphon therein.
  • Evaporator 15 has a plurality of fins 16 each in the form of a flat plate to exchange heat over an increased area. Furthermore, to allow the coolant's evaporation and condensation and resultant natural circulation to be utilized, evaporator 15 is arranged to be lower than condenser 12 . Below condenser 15 is arranged a drain plate 17 to reserve drainage condensed on and dropping from a surface of evaporator 15 .
  • Heat transfer cycle 4 associated with the heated portion is a thermosyphon employing water, hydrocarbon or a similar natural coolant, and generally a circulation circuit including an evaporator 6 associated with the heated portion and attached to Stirling refrigerating machine 1 at heated portion 2 , a condenser 8 associated with the heated portion and arranged to be higher than evaporator 6 to condense the natural coolant, and a vapor coolant pipe 7 and a condensate coolant pipe 11 connecting evaporator 6 and condenser 8 together to circulate the coolant.
  • the circuit has water (including an aqueous solution), hydrocarbon or a similar natural coolant sealed therein as the coolant.
  • condensate coolant pipe 11 is connected to evaporator 6 at a topmost end.
  • Condenser 8 has a plurality of fins 18 each in the form of a flat plate attached thereto to exchange heat over an increased area and behind condenser 8 is provided a pair of heat radiating fans 19 operated to externally discharge heat.
  • FIG. 21 is a perspective view specifically showing a structure of the heat transfer cycle associated with the heated portion in the cooling apparatus described as the second conventional example.
  • heat transfer cycle 4 will further more specifically be described in structure.
  • Evaporator 6 as a whole forms a ring, which is adapted to have a structure formed of two semi-rings 6 A and 6 B joined together along the ring's diameter to help to attach evaporator 6 to Stirling refrigerating machine 1 at heated portion 2 .
  • Each semi-ring 6 A, 6 B is an arc having opposite ends or surfaces closed.
  • Semi-rings 6 A and 6 B are arranged to surround heated portion 2 and joined together vertically thereabove and therebelow, and have their respective lower ends connected by a U-letter communication pipe 6 C for communication.
  • Semi-rings 6 A and 6 B have their internal coolant's condensate communicated through connection pipe 6 C and thus mixed together.
  • Vapor coolant pipe 7 is formed of two vertical pipes 7 A and 7 B connected to semi-rings 6 A and 6 B, respectively, and a lateral pipe 7 C (also referred to as a header pipe) connected to vertical pipes 7 A and 7 B.
  • Vertical pipes 7 A and 7 B are connected to semi-rings 6 A and 6 B at their respective outer circumferential, upper ends, respectively, and lateral pipe 7 C at a bottommost portion vertically.
  • Lateral pipe 7 C has longitudinally opposite end surfaces closed and is arranged in a direction orthogonal to an axis of Stirling refrigerating machine 1 and horizontally.
  • Condensate coolant pipe 11 is similar in structure to pipe 7 , although to form a thermosyphon, vapor coolant pipe 7 has lateral pipe 7 C arranged at a position higher than a lateral pipe 111 C of condensate coolant pipe 11 , and to efficiently operate the thermosyphon, the vertical and lateral pipes are both relatively larger in diameter for vapor coolant pipe 7 than condensate coolant pipe 11 .
  • Condenser 8 is formed of six serpentine tubes 8 A- 8 F arranged in parallel in the longitudinal direction of lateral pipes 7 C and 11 C, or horizontally.
  • Serpentine tubes 8 A- 8 F each have one end connected to lateral pipe 7 C and the other end to lateral pipe 11 C and together connect lateral pipes 7 C and 11 C together equally in their longitudinal direction.
  • the plurality of fins 18 are arranged at a linear portion of serpentine tubes 8 A- 8 F in parallel and thermally coupled therewith.
  • Heat transfer cycle 4 operates as described hereinafter. Heated portion 2 generates heat which is in turn transferred from around heated portion 2 to evaporator 6 and evaporates the coolant in semi-rings 6 A and 6 B.
  • the coolant evaporated in semi-ring 6 A and that evaporated in semi-ring 6 B ascend through the vapor coolant pipe 7 vertical pipes 7 A and 7 B, respectively, and are joined in lateral pipe 7 C and then branched to flow into serpentine tubes 8 A- 8 F.
  • the coolant's vapor passes through condenser 8 arranged at a position higher than evaporator 6 and exchanges heat via fin 18 with the surrounding ambient and thus becomes a condensate.
  • condensate (or that having gas mixed together) conflows in condensate coolant pipe 11 at lateral pipe 11 C and furthermore branches to vertical pipes 11 A and 11 B and flows downward to return to evaporator 6 and is again evaporated by heat of heated portion 2 .
  • a significantly larger amount of heat is transferred than by utilizing exchange heat through sensible heat. This allows heat to be exchanged significantly effectively.
  • a difference in level between condenser 8 and evaporator 6 vertically arranged and a difference in specific gravity between gas and liquid provide a difference in pressure providing a driving force to circulate the coolant. This can eliminate the necessity of employing a pump or a similar external force to circulate the coolant and thus save energy.
  • Patent Document 1 Japanese Patent Laying-Open No. 2003-050073
  • Patent Document 2 Japanese Patent Laying-Open No. 2001-033139
  • Patent Document 3 Japanese Patent Laying-Open No. 2003-302117
  • first conventional example's loop thermosyphon 100 I often has condenser 130 I with a variety of pipes and radiating fins combined together in an assembly and thus unitized and thus fabricated. More specifically, it is fabricated as an assembly formed of a header pipe 131 associated with a feed pipe and branching a working fluid introduced through a feed pipe 120 , a header pipe 132 associated with a return pipe and allowing the branched working fluid to rejoin, a plurality of aligned pipes 133 extending in the same direction and connecting header pipes 131 and 132 together (see FIG. 18 ), and a radiating fin (not shown) assembled in contact with the plurality of aligned pipes 133 .
  • the plurality of aligned pipes 133 each have linear portions 134 a - 134 d extending linearly in one direction and arranged in parallel in layers to form a plurality of vertically arranged stages (in FIG. 18 , four stages), and curved portions 135 a - 135 c connecting linear portions 134 a - 134 d together.
  • each aligned pipe 133 is formed to be a serpentine tube as shown in FIG. 18 .
  • the plurality of linear portions 134 a - 134 d are arranged in parallel layers mainly in order to facilitate fabrication and also ensures a maximum heat transfer area with a smaller space.
  • Condenser 130 I implemented by the assembly thus configured is arranged in equipment (e.g., a Stirling refrigerator) having loop thermosyphon 100 I mounted, at a casing 300 above a bottom surface 301 , as shown in FIG. 17 . Note that condenser 130 I implemented by the assembly is arranged parallel to bottom surface 301 .
  • equipment e.g., a Stirling refrigerator
  • condenser 130 I When the equipment having loop thermosyphon 100 I mounted has casing 300 with bottom surface 301 parallel to a surface on which it is disposed, or a floor surface 401 , as shown in FIG. 18 , condenser 130 I has aligned pipe 133 with linear portions 134 a - 134 d also parallel to floor surface 401 . In that case, the working fluid condensed and thus liquefied in condenser 130 I at aligned pipe 133 smoothly flows through aligned pipe 133 and is delivered through header pipe 132 and return pipe 140 to evaporator 110 . Note that in the figure the working fluid flows in a direction indicated by an arrow 500 .
  • the equipment is disposed such that the casing has the bottom surface parallel to the floor surface, it does not cause a particular problem. If the casing has the bottom surface inclined relative to a horizontal floor surface or a floor surface itself is inclined and the casing is arranged parallel to the inclined floor surface, however, the loop thermosyphon will also be inclined relative to horizon and the working fluid's flow can be significantly affected thereby.
  • condenser 130 I having aligned pipe 133 with linear portions 134 a - 134 d also parallel to the casing 300 bottom surface 301 , will be inclined relative to the horizontal plane by angle ⁇ 0 .
  • the shown condition shows that the equipment's casing 300 inclined and thus arranged so that the bottommost stage or linear portion 134 d has an end adjacent to curved portion 135 c lower in level than that adjacent to header pipe 132 associated with the return pipe.
  • condenser 130 I If in that condition condenser 130 I is arranged, the working fluid condensed and thus liquefied in condenser 130 I at the bottommost stage or linear portion 134 d is pulled by gravity and thus flows back and will stay in the bottommost stage or linear portion 134 d closer to curved portion 135 c .
  • the condensed working fluid 502 will not flow into header pipe 132 associated with the return pipe, and as the equipment operates, working fluid 502 is gradually accumulated and finally will have a level 503 raised to close aligned pipe 133 .
  • thermosyphon can provide a defective operation depending on how it is arranged, and this has been a significantly serious issue to be addressed.
  • cooling apparatus 50 including Stirling refrigerating machine 1 is itself assembled independently and thereafter mounted in a refrigerator (not shown) and thus shipped as a product. Note that cooling apparatus 50 is incorporated so that when the refrigerator is disposed at a horizontal place lateral pipes 7 C and 11 C are horizontal.
  • the second conventional example's cooling apparatus it cannot be expected that the user ensures that the refrigerator is disposed at a horizontal place, and in reality the refrigerator can be placed at a slanting place.
  • the entirety of the system will be inclined relative to the horizontal plane, and condensate coolant pipe 11 will have a condensate coolant 20 staying in a lateral pipe 11 C at a portion lower than an upper end of a vertical pipe (in FIG. 22, 11B ) lower in the direction of gravity.
  • the coolant circulates in a reduced amount resulting in impaired heat radiation efficiency.
  • the present invention contemplates a loop thermosyphon capable of preventing defective operation regardless of disposition, and a Stirling refrigerator equipped therewith.
  • the present invention also contemplates a cooling apparatus capable of reliably circulating a coolant in a heat transfer cycle associated with a heated portion of a Stirling refrigerating machine if the apparatus is inclined.
  • a loop thermosyphon in a first aspect of the present invention is mounted at a casing of equipment having a heat source, and employs a working fluid enclosed in a closed circuit to externally radiate heat from the heat source.
  • a “loop thermosyphon mounted at a casing” as referred to herein includes a loop thermosyphon entirely accommodated in the casing and a loop thermosyphon partially accommodated in the casing and partially exposed.
  • the closed circuit includes: an evaporator depriving the heat source of heat to evaporate the working fluid; a condenser condensing the working fluid evaporated at the evaporator; a feed pipe feeding to the condenser the working fluid evaporated at the evaporator; and a return pipe returning to the evaporator the working fluid condensed at the condenser.
  • the condenser has a serpentine tube having a linear portion extending in one direction and forming a plurality of stages in layers, and a curved portion connecting such linear portions together, and the serpentine tube has a bottommost one of the linear portions inclined in a direction allowing the bottommost linear portion to be closer to a bottom surface of the casing as the bottommost linear portion approaches the return pipe.
  • a loop thermosyphon in a second aspect of the present invention is mounted at a casing of equipment having a heat source, and employs a working fluid enclosed in a closed circuit to externally radiate heat from the heat source.
  • the closed circuit includes: an evaporator depriving the heat source of heat to evaporate the working fluid; a condenser condensing the working fluid evaporated at the evaporator; a feed pipe feeding to the condenser the working fluid evaporated at the evaporator; and a return pipe returning to the evaporator the working fluid condensed at the condenser.
  • the condenser is an assembly including a header pipe associated with the feed pipe, and connected to the feed pipe to branch the working fluid introduced thereinto, a header pipe associated with the return pipe, and connected to the return pipe and joining together the working fluid branched, and a plurality of aligned pipes extending in a same direction and connecting the header pipes together.
  • the aligned pipes are each a serpentine tube having a linear portion extending in one direction and forming a plurality of stages in layers, and a curved portion connecting such linear portions together.
  • the assembly or condenser is entirely inclined relative to a bottom surface of the casing such that of the linear portions, a bottommost linear portion is inclined in a direction allowing the bottommost linear portion to be closer to the bottom surface as the bottommost linear portion approaches the header pipe associated with the return pipe.
  • the condenser is fabricated to be a unit such that the serpentine tube has the linear portion arranged in vertically parallel layers, the possibility that the working fluid condensed and liquefied will stay in the serpentine tube can nonetheless be reduced.
  • the loop thermosyphon's defective operation attributed to disposition can thus be reduced.
  • the condenser is arranged to incline relative to the bottom surface of the casing at an angle larger than 0° and at most 6°.
  • the condenser that is previously inclined to satisfy such condition can significantly prevent the loop thermosyphon's defective operation attributed to disposition.
  • the header pipe associated with the return pipe extends in a second direction traversing the first direction
  • the return pipe is connected in a vicinity of one end of the header pipe associated with the return pipe and extending in the second direction
  • the header pipe associated with the return pipe is inclined in a direction allowing the header pipe associated with the return pipe to be closer to the bottom surface of the casing as the header pipe associated with the return pipe extends toward the one end from the other end positionally opposite the one end.
  • a loop thermosyphon in a third aspect of the present invention is mounted at a casing of equipment having a heat source, and employs a working fluid enclosed in a closed circuit to externally radiate heat from the heat source.
  • the closed circuit includes: an evaporator depriving the heat source of heat to evaporate the working fluid; a condenser condensing the working fluid evaporated at the evaporator; a feed pipe feeding to the condenser the working fluid evaporated at the evaporator; and a return pipe returning to the evaporator the working fluid condensed at the condenser.
  • the condenser is an assembly including a header pipe associated with the feed pipe, and connected to the feed pipe to branch the working fluid introduced thereinto, a header pipe associated with the return pipe, and connected to the return pipe and joining together the working fluid branched, and a plurality of aligned pipes extending in a same direction and connecting the header pipes together.
  • the header pipe associated with the return pipe extends in one direction.
  • the return pipe is connected in a vicinity of one end of the header pipe associated with the return pipe and extending in the one direction.
  • the header pipe associated with the return pipe is inclined in a direction allowing the header pipe associated with the return pipe to be closer to a bottom surface of the casing as the header pipe associated with the return pipe extends toward the one end from the other end positionally opposite the one end.
  • a loop thermosyphon in a fourth aspect of the present invention is mounted at a casing of equipment having a heat source, and employs a working fluid enclosed in a closed circuit to externally radiate heat from the heat source.
  • the closed circuit includes: an evaporator depriving the heat source of heat to evaporate the working fluid; a condenser condensing the working fluid evaporated at the evaporator; a feed pipe feeding to the condenser the working fluid evaporated at the evaporator; and a return pipe returning to the evaporator the working fluid condensed at the condenser.
  • the condenser is an assembly including a header pipe associated with the feed pipe, and connected to the feed pipe to branch the working fluid introduced thereinto, a header pipe associated with the return pipe, and connected to the return pipe and joining together the working fluid branched, and a plurality of linear tubes arranged in parallel and connecting the header pipes together.
  • the linear tubes are each inclined in a direction allowing each the linear tube to be closer to a bottom surface of the casing as each the linear tube approaches the header pipe associated with the return pipe.
  • a condenser that has a linear tube, rather than a serpentine tube, connecting together header pipes associated with feed and return pipes, respectively, the condenser will not have a working fluid convected in the pipe, and the loop thermosyphon's defective operation attributed to disposition can thus be reduced.
  • the present Stirling refrigerator is a Stirling refrigerator having a Stirling refrigerating machine mounted.
  • the Stirling refrigerating machine includes any of the loop thermosyphons in the first to fourth aspects of the present invention and the loop thermosyphon has an evaporator configured to exchange heat with a heated portion of the Stirling refrigerating machine.
  • the Stirling refrigerator thus configured is not affected in performance by how a casing is disposed.
  • a cooling apparatus in a first aspect of the present invention has a heat transfer cycle associated with a cold portion and extracting cold generated by a Stirling refrigerating machine at the cold portion, and a heat transfer cycle associated with a heated portion and externally radiating hot generated by the Stirling refrigerating machine at the heated portion.
  • the heat transfer cycle associated with the heated portion includes an evaporator associated with the heated portion and attached to the Stirling refrigerating machine at the heated portion and a condenser associated with the heated portion and arranged to be higher in level than the evaporator, with a vapor coolant pipe and a condensate coolant pipe connecting the evaporator and the condenser to form a coolant circulation circuit, and the condensate coolant pipe includes a lateral pipe having opposite ends closed and connected to the condenser and a pair of vertical pipes vertically connecting the evaporator and the lateral pipe together, the pair of vertical pipes having one and the other, upper ends connected to the lateral pipe at one and the other ends, respectively. If the cooling apparatus is inclined, the heat transfer cycle associated with the heated portion will not have the coolant's condensate staying in the lateral pipe.
  • the vertical pipe has an upper end with a lateral pipe connected thereto and a lower end with the evaporator associated with the heated portion connected thereto, however, the connections' ports do riot necessarily, positionally match with each other as seen horizontally. Accordingly, the vertical pipe is provided with an inclined portion having a downward gradient.
  • a refrigerator is installed at a place having an inclination within 5° for safety, and providing the vertical pipe with an inclined portion having a downward gradient of at least 5° with reference to the cooling apparatus placed in a horizontal position allows the downward gradient to be maintained if the cooling apparatus is inclined, and the coolant's condensate can be prevented from clogging.
  • a cooling apparatus in a second aspect of the present invention has a heat transfer cycle associated with a cold portion and extracting cold generated by a Stirling refrigerating machine at the cold portion, and a heat transfer cycle associated with a heated portion and externally radiating hot generated by the Stirling refrigerating machine at the heated portion.
  • the heat transfer cycle associated with the heated portion includes an evaporator associated with the heated portion and attached to the Stirling refrigerating machine at the heated portion and a condenser associated with the heated portion and arranged to be higher in level than the evaporator, with a vapor coolant pipe and a condensate coolant pipe connecting the evaporator and the condenser to form a coolant circulation circuit.
  • the condensate coolant pipe includes a lateral pipe having opposite ends closed and connected to the condenser and a pair of vertical pipes vertically connecting the evaporator and the lateral pipe together
  • the vapor coolant pipe includes a lateral pipe having opposite ends closed and connected to the condenser and a pair of vertical pipes vertically connecting the evaporator and the lateral pipe together.
  • the lateral pipe of the vapor coolant pipe is arranged to be higher in level than the lateral pipe of the condenser coolant pipe and a degassing charge pipe is attached to the vapor coolant pipe at the lateral pipe.
  • the charge pipe attached at such a high position can prevent water from being sucked in vacuuming and also contribute to improved efficiency in vacuuming.
  • the loop thermosyphon in the first to fourth aspects of the present invention can be prevented from defective operation regardless of disposition. Furthermore the Stirling refrigerator of the present invention can exhibit high performance regardless of how the casing is disposed.
  • a heated portion generates heat, which is transferred and externally radiated by a thermosyphon utilized in a heat transfer cycle associated with the heated portion and having a condensate coolant pipe passing the coolant's condensate naturally downward toward an evaporator associated with the heated portion, that is configured of a lateral pipe having opposite ends closed and disposed at an outlet of a condenser associated with the heated portion and a pair of vertical pipes vertically connecting together the lateral pipe and the evaporator associated with the heated portion, with each vertical pipe having an upper end connected to the lateral pipe at one and the other ends, respectively.
  • the cooling apparatus is inclined, the coolant's condensate does not stay in the lateral pipe of the heat transfer cycle associated with the heated portion. The cycle can thus circulate the coolant reliably.
  • FIG. 1 is a schematic, perspective view of a structure of the present loop thermosyphon in the first embodiment installed.
  • FIG. 2 schematically shows a configuration of a condenser of the FIG. 1 loop thermosyphon.
  • FIGS. 3A and 3B schematically show how the condenser of the present loop thermosyphon in the first embodiment is installed, with the loop thermosyphon seen in front and side views, respectively.
  • FIG. 4 shows how a working fluid flows in the first embodiment when the condenser inclines relatives to a horizontal plane.
  • FIG. 5 shows how a working fluid flows in the first embodiment when the condenser inclines relatives to a horizontal plane.
  • FIGS. 6A and 6B schematically show how the condenser of the present loop thermosyphon in a second embodiment is installed, with the loop thermosyphon seen in front and side views, respectively.
  • FIGS. 7A and 7B schematically show how the condenser of the present loop thermosyphon in a third embodiment is installed, with the loop thermosyphon seen in front and side views, respectively.
  • FIG. 8 schematically shows a configuration of a condenser of the present loop thermosyphon in a fourth embodiment.
  • FIG. 9 schematically shows how the present loop thermosyphon in the fourth embodiment is installed, as seen in a side view.
  • FIGS. 10-13 schematically show configurations of the present loop thermosyphon in fifth to eighth embodiments, respectively.
  • FIG. 14 is a schematic cross section of a structure of the present Stirling refrigerator in a ninth embodiment.
  • FIG. 15 is a perspective view specifically showing a structure of a heat transfer cycle associated with a heated portion in a tenth embodiment of the present invention.
  • FIGS. 16A and 16B are front and side views, respectively, of the heat transfer cycle associated with the heated portion in the tenth embodiment.
  • FIGS. 17A and 17B schematically show a structure of a loop thermosyphon in a first conventional example, as seen in front and side views, respectively.
  • FIG. 18 schematically shows a structure of a condenser of the loop thermosyphon in the first conventional example, showing how a working fluid flows with the condenser disposed horizontally.
  • FIG. 19 shows how the working fluid flows with the FIG. 18 condenser inclined relative to a horizontal plane.
  • FIG. 20 is a side view schematically showing a structure of a cooling apparatus in a second conventional example.
  • FIG. 21 is a perspective view specifically showing a structure of a heat transfer cycle associated with a heated portion of the cooling apparatus of the second conventional example.
  • FIG. 22 is a front view of a main portion of the heat transfer cycle associated with the heated portion with the FIG. 20 , second conventional example's cooling apparatus inclined.
  • FIG. 1 Initially reference will be made to FIG. 1 to describe a loop thermosyphon in the present embodiment and a structure of a Stirling refrigerating machine installed with the loop thermosyphon attached thereto.
  • a Stirling refrigerating machine 200 is placed on a supporting platform 250 and supported by supports 254 a , 254 b provided on platform 250 at a bottom plate 252 . Furthermore, a loop thermosyphon 100 A is also placed on platform 250 and supported thereon by support 254 a , 254 c provided at a bottom plate 252 . Stirling refrigerating machine 200 and loop thermosyphon 100 A supported by platform 250 are disposed in a casing of prescribed equipment (e.g., a refrigerator). Note that platform 250 has bottom plate 252 parallel to a bottom surface of the casing of the equipment.
  • prescribed equipment e.g., a refrigerator
  • Stirling refrigerating machine 200 is structured and operates, as described hereinafter.
  • Stirling refrigerating machine 200 includes a pressure chamber 202 provided therein with a cylinder having a piston and a displacer fitted and thus attached thereto.
  • the cylinder is filled with helium or a similar working medium.
  • the cylinder has an internal space sectioned by the piston and the displacer to provide a compression section and an expansion section.
  • the compression section is surrounded by a heated portion 204 and the expansion section is surrounded by a cold portion 206 .
  • the piston fitted in the cylinder is driven by a linear actuator to reciprocate in the cylinder.
  • the displacer reciprocates in the cylinder with a constant phase difference from the piston's reciprocation.
  • an inverted Stirling cycle is implemented in the cylinder.
  • heated portion 204 surrounding the compression section rises in temperature
  • cold portion 206 surrounding the expansion section is cooled to cryogenic temperature.
  • Loop thermosyphon 100 A has a structure and operates as described hereinafter.
  • loop thermosyphon 100 A includes an evaporator 110 and a condenser 130 A.
  • Evaporator 110 is arranged in contact with heated portion 204 of Stirling refrigerating machine 200 to deprive heated portion 204 of heat to evaporate a working fluid introduced in evaporator 110 .
  • Condenser 130 A is arranged at a position higher than evaporator 110 to condense the working fluid evaporated at evaporator 110 .
  • Evaporator 110 and condenser 130 A are connected by a feed pipe 120 and a return pipe 140 to together form a closed circuit.
  • a heat source, or heated portion 204 has a cylindrical geometry. Accordingly, evaporator 110 is formed of two arcuate components.
  • condenser 130 A is formed of a header pipe 131 associated with the feed pipe, a header pipe 132 associated with the return pipe, a plurality of aligned pipes 133 connecting headers 131 and 132 , and a radiating fin 136 provided in contact with aligned pipes 133 , assembled together to be a unit.
  • Header pipe 131 is a distributor connected to feed pipe 120 to branch the working fluid introduced.
  • header pipe 132 is connected to return pipe 140 to collect pipes to join branches of the working fluid together.
  • aligned pipe 133 is each defined by linear portions 134 a - 134 d (in four stages for condenser 130 A in the present embodiment) linearly extending in a first direction (in the figure, a direction A), and curved portions 135 a - 135 c connecting linear portions 134 a - 134 d .
  • Linear portions 134 a - 134 d are arranged, one on another, vertically in parallel.
  • Curved portions 135 a - 135 c connect linear portions 134 a - 134 d at their respective ends together.
  • condenser 130 A is configured of aligned pipes 133 configured of laterally arranged serpentine tubes.
  • the plurality of aligned pipes 133 at linear portions 134 a - 134 d have a plurality of radiating fins 136 assembled thereto.
  • evaporator 110 the working fluid deprives heated portion 204 of Stirling refrigerating machine 200 of heat and thus evaporates, and ascends by a vapor pressure difference between evaporator 110 and condenser 130 A against gravity through feed pipe 120 and enters condenser 130 A.
  • Condenser 130 A cools and thus condenses the working fluid, which is in turn pulled by gravity, and thus descends through return pipe 140 and enters evaporator 110 .
  • Such convection of the working fluid involving a change in phase as described above allows heated portion 204 to externally radiate heat.
  • loop thermosyphon 100 A has condenser 130 A arranged as described hereinafter.
  • the present embodiment loop thermosyphon 100 A has condenser 130 A arranged to incline relative to bottom surface 301 of casing 300 of a refrigerator or similar equipment. More specifically, condenser 130 A formed of an assembly is arranged to incline by an angle ⁇ 1 so that an end of condenser 130 A that is closer to header pipe 132 is closer to bottom surface 301 than that of condenser 130 A farther away from header pipe 132 is
  • condenser 130 A is arranged to entirely incline by angle ⁇ 1 to have aligned serpentine tube 133 with the bottommost linear portion 134 d inclined to be closer to bottom surface 301 as the serpentine tube approaches header pipe 132 .
  • Condenser 130 A is inclined relative to bottom surface 301 by angle ⁇ 1 preferably of larger than 0° and at most 6°, more preferably approximately 3°. This can be done for example by adjusting support 254 c of supporting platform 250 in height (see FIG. 1 ).
  • condenser 130 A previously arranged to incline relative to bottom surface 301 by angle ⁇ 1 , will also be arranged to incline relative to a horizontal plane by angle ⁇ 1 .
  • aligned pipe 133 passes the working fluid, which is condensed and liquefied in the bottommost stage's linear portion 134 d , and pulled by gravity to flow through the inclined linear portion 134 d toward header pipe 132 and thus flow out of aligned pipes 133 . Consequently, aligned pipe 133 will not have the working fluid staying therein. Thus the working fluid can smoothly flow and loop thermosyphon 100 A can reliably operate.
  • casing 300 having bottom surface 301 inclined relative to a horizontal floor surface.
  • equipment has casing 300 inclined in a direction B.
  • condenser 130 A after installation will have an inclination of an angle larger than angle ⁇ 1 relative to the horizontal plane.
  • the working fluid flowing in condenser 130 A through aligned pipe 133 is condensed and liquefied mainly at the bottommost linear portion 134 d , and pulled by gravity to flow through the inclined linear portion 134 d toward header pipe 132 and flows out of aligned pipes 133 .
  • aligned pipe 133 will not have the working fluid staying therein.
  • the working fluid can smoothly flow and loop thermosyphon 100 A can reliably operate.
  • aligned pipe 133 occasionally has the working fluid condensed and liquefied not only at the bottommost linear portion 134 d but also linear portion 134 c immediately overlying linear portion 134 d . In that case, the condensed working fluid may stay in a vicinity of curved portion 135 b adjacent to linear portion 134 c and thus close aligned pipe 133 .
  • Such phenomenon occurs at a critical angle of approximately 6°, as confirmed by the inventor, although it slightly varies depending on how condenser 130 A is designed in dimension or the like.
  • equipment has casing 300 inclined in a direction C by an angle ⁇ 1 , wherein ⁇ 1 ⁇ 1 .
  • casing 300 thus inclined, condenser 130 A after it is arranged will incline by an angle ⁇ 1 - ⁇ 1 relative to a horizontal plane.
  • the working fluid flowing in condenser 130 A through aligned pipe 133 is condensed and liquefied mainly at the bottommost linear portion 134 d .
  • condenser 130 A is inclined relative to the horizontal plane by angle ⁇ 1 - ⁇ 1 . Accordingly the working fluid liquefied in the bottommost linear portion 134 d flows through linear portion 134 d toward header pipe 132 and flows out of aligned pipes 133 .
  • aligned pipe 133 will not have the working fluid staying therein.
  • the working fluid can smoothly flow and loop thermosyphon 100 A can reliably operate.
  • casing 300 thus inclined, condenser 130 A after it is disposed will be arranged horizontally.
  • the working fluid flowing in condenser 130 A through aligned pipe 133 is condensed and liquefied mainly at the bottommost linear portion 134 d .
  • the convection of the working fluid caused in aligned pipe 133 allows the liquefied working fluid to flow toward header pipe 132 and flow out of aligned pipe 133 .
  • aligned pipe 133 will not have the working fluid staying therein.
  • the working fluid can smoothly flow and loop thermosyphon 100 A can reliably operate.
  • equipment has casing 300 inclined in direction C by an angle ⁇ 3 , wherein ⁇ 3 > ⁇ 1 .
  • casing 300 thus inclined, condenser 130 A after it is arranged will incline by an angle ⁇ 3 - ⁇ 1 relative to the horizontal plane.
  • the working fluid flowing in condenser 130 A through aligned pipe 133 is condensed and liquefied mainly at the bottommost linear portion 134 d .
  • the working fluid liquefied in linear portion 134 d is pulled by gravity to flow through linear portion 134 d to move away from header pipe 132 .
  • the liquefied working fluid 502 will stay in the bottommost linear portion 134 d closer to curved portion 135 c.
  • thermosyphon can reliably operate, and as a result the Stirling refrigerating machine can be protected against damage attributed to unexpected defective operation, and can also have a heated portion reliably cooled and hence operate significantly efficiently.
  • the present embodiment provides a loop thermosyphon 100 B also utilized as a heat transfer system associated with a heated portion of a Stirling refrigerating machine, similarly as described in the first embodiment. Accordingly, the components similar to those of the first embodiment are shown in the figures with identical reference characters.
  • the present embodiment provides loop thermosyphon 100 B with a condenser 130 B similar to condenser 130 A of loop thermosyphon 100 A described in the first embodiment. More specifically, condenser 130 B is unitized as an assembly formed of header pipe 131 associated with a feed pipe, header pipe 132 associated with a return pipe, the plurality of aligned pipes 133 connecting header pipes 131 and 132 together, and a radiating fin 136 provided in contact with aligned pipes 133 .
  • Aligned pipe 133 has a linear portion extending in a first direction (indicated in the figure by an arrow A), and header pipe 132 associated with the return pipe extends in a second direction (indicated in the figure by an arrow E) traversing the first direction.
  • Return pipe 140 is connected in a vicinity of one end of header pipe 132 extending in this one direction.
  • Condenser 130 B is arranged to incline relative to bottom surface 301 of casing 300 of a refrigerator or similar equipment. More specifically, condenser 130 B formed of an assembly is arranged to entirely incline by an angle ⁇ 2 such that one end having return pipe 140 connected thereto is positioned to be closer than the other end corresponding to that opposite to one end.
  • condenser 130 B is arranged to entirely incline by angle ⁇ 2 such that condenser 130 A has header pipe 132 inclined in a direction allowing header pipe 132 to have a smaller distance to bottom surface 301 for one end having return pipe 140 connected thereto than the other end located opposite to one end.
  • condenser 130 B is not particularly limited in inclination or angle ⁇ 2 , although it is preferably several degrees to an angle between 10 degrees and 20 degrees. Such inclination can be done for example by adjusting in geometry an upper and of support 254 c of supporting platform 250 (see FIG. 1 ).
  • the working fluid condensed and liquefied in the plurality of aligned pipes 133 flows through each aligned pipe 133 into header pipe 132 and thus joins to flow together, and further flows through return pipe 140 into evaporator 110 .
  • header pipe 132 is arranged parallel to bottom surface 301 , header pipe 132 is not necessarily arranged horizontally, depending on how casing 300 is arranged relative to a floor surface, how the floor surface inclines, and the like. Accordingly, as shown in FIG. 17 , a conventional loop thermosyphon has return pipe 140 connected to header pipe 132 at a center to provide a minimum distance to each aligned pipe 133 to allow the working fluid to smoothly flow.
  • header pipe 132 is arranged to incline, the working fluid is more, significantly prevented from flowing in header pipe 132 at a location lower than the portion connecting header pipe 132 and return pipe 140 together than at a location higher than that portion. Consequently in the plurality of aligned pipes 133 the working fluid experiences different flow resistances and the loop thermosyphon cannot operate efficiently.
  • loop thermosyphon 100 B has header pipe 132 arranged to previously incline relative to bottom surface 301 of casing 300 of equipment and has return pipe 140 connected to header pipe 132 at an end closer to bottom surface 301 to allow the working fluid to smoothly flow.
  • the loop thermosyphon can be prevented from defective operation attributed to disposition and thus reliably operate.
  • the present embodiment provides a loop thermosyphon 100 C also utilized as a heat transfer system associated with a heated portion of a Stirling refrigerating machine, similarly as described in the first or second embodiment. Accordingly, the components similar to those of the first or second embodiment are shown in the figures with identical reference characters.
  • the present embodiment provides loop thermosyphon 100 C with a condenser 130 C similar to condensers 130 A and 130 B of loop thermosyphons 100 A and 1001 B described in the first and second embodiments. More specifically, condenser 130 C is unitized as an assembly formed of header pipe 131 associated with a feed pipe, header pipe 132 associated with a return pipe, the plurality of aligned pipes 133 connecting header pipes 131 and 132 together, and radiating fin 136 provided in contact with aligned pipes 133 .
  • condenser 130 C is arranged to entirely incline by angle ⁇ 1 to have aligned serpentine tube 133 with linear portions 134 a - 134 d inclined to be closer to bottom surface 301 as the serpentine tube approaches header pipe 132 .
  • condenser 130 B is arranged to entirely incline by angle ⁇ 2 such that header pipe 132 is inclined in a direction allowing header pipe 132 to have a smaller distance to bottom surface 301 for one end having return pipe 140 connected thereto than the other end located opposite to one end.
  • the effect of the first embodiment and that of the second embodiment can both be achieved.
  • This can significantly reduce a defective operation of the loop thermosyphon attributed to disposition.
  • the loop thermosyphon can reliably operate and the Stirling refrigerating machine can be operated highly efficiently.
  • the present embodiment provides a loop thermosyphon 100 D also utilized as a heat transfer system associated with a heated portion of a Stirling refrigerating machine, similarly as described in the first to third embodiments. Accordingly, the components similar to those of the first to third embodiments are shown in the figures with identical reference characters.
  • loop thermosyphon 100 D has a condenser 130 D with each aligned pipe 133 defined by linear portions 134 a - 134 e linearly extending in a first direction (in the figure, direction A), and curved portions 135 a - 135 d connecting linear portions 134 a - 134 e .
  • Linear portions 134 a - 134 e are arranged, one on another, vertically in parallel.
  • Curved portions 135 a - 135 d connect linear portions 134 a - 134 e at their respective ends together.
  • condenser 130 D is configured of aligned pipes 133 configured of laterally arranged serpentine tubes.
  • the plurality of aligned pipes 133 at linear portions 134 a - 134 e have a plurality of radiating fins 136 assembled thereto.
  • condenser 130 D needs to be arranged to incline to have its rear side to be closer to bottom surface 301 .
  • This allows aligned serpentine tubes 133 to have linear portions 134 a - 134 e inclined in a direction allowing them to have a smaller distance to bottom surface 301 as they approach header pipe 132 .
  • Condenser 130 D can be arranged to incline relative to bottom surface 301 of casing 300 for example by adjusting support 254 C of support platform 250 in height (see FIG. 1 ).
  • a condenser having aligned pipes 133 in an odd number of stages in layers that is entirely inclined relative to a bottom surface of a casing by angle ⁇ 1 also allows a loop thermosyphon to reliably operate regardless of how the casing is disposed.
  • the present embodiment provides a loop thermosyphon 100 E also utilized as a heat transfer system associated with a heated portion of a Stirling refrigerating machine, similarly as described in the first to fourth embodiments. Accordingly, the components similar to those of the first to fourth embodiments are shown in the figures with identical reference characters.
  • loop thermosyphon 100 E has a condenser 130 E with aligned pipes 133 each defined by linear portions 134 a - 134 c linearly extending in a first direction (in the figure, direction A) parallel to bottom surface 301 of casing 300 of equipment, linear portion 134 d located at a bottommost stage and inclined relative to bottom surface 301 , and curved portions 135 a - 135 c connecting linear portions 134 a - 134 d .
  • Linear portions 134 a - 134 d have their respective ends connected together by curved portions 135 a - 135 c .
  • the plurality of aligned pipes 133 at linear portions 134 a - 134 d have a plurality of radiating fins 136 assembled thereto.
  • Condenser 130 E has the bottommost linear portion 134 d inclined in a direction allowing linear portion 134 d to have a smaller distance to bottom surface 301 as linear portion 134 d approaches header pipe 132 .
  • linear portion 134 d is inclined relative to bottom surface 301 by an angle ⁇ 3 .
  • the working fluid flowing in condenser 130 E through aligned pipe 133 is condensed and liquefied mainly at the bottommost linear portion 134 d and pulled by gravity to flow through the inclined linear portion 134 d toward header pipe 132 and flow out of aligned pipe 133 .
  • aligned pipe 133 will not have the liquefied working fluid staying therein.
  • the bottommost linear portion 134 d previously alone inclined relative to bottom surface 301 of casing 300 by a prescribed angle allows the working fluid to smoothly flow regardless of how the casing is disposed, and loop thermosyphon 100 E can reliably operate.
  • the present embodiment provides a loop thermosyphon 100 F also utilized as a heat transfer system associated with a heated portion of a Stirling refrigerating machine, similarly as described in the first to fifth embodiments. Accordingly, the components similar to those of the first to fifth embodiments are shown in the figures with identical reference characters.
  • the present embodiment provides loop thermosyphon 100 F having a condenser 130 F with the plurality of aligned pipes 133 each defined by linearly extending portions 134 a - 134 d and curved portions 135 a - 135 c connecting linear portions 134 a - 134 d together.
  • Linear portions 134 a - 134 d have their respective ends connected together by curved portions 135 a - 135 c .
  • the plurality of aligned pipes 133 at linear portions 134 a - 134 d have a plurality of radiating fins 136 assembled thereto.
  • Condenser 130 E has linear portions 134 a - 134 d each arranged to incline in a direction allowing linear portions 134 a - 134 d to have a smaller distance to bottom surface 301 of casing 300 of the equipment as the linear portions extend downstream (or extend from header pipe 131 toward header pipe 132 ).
  • the bottommost linear portion 134 d is inclined relative to bottom surface 301 by an angle ⁇ 4 .
  • aligned pipe 133 The working fluid flowing in condenser 130 E through aligned pipe 133 is condensed and liquefied mainly at the bottommost linear portion 134 d .
  • aligned pipe 133 occasionally has the working fluid condensed and liquefied not only at the bottommost linear portion 134 d but also linear portions 134 a - 134 c overlying linear portion 134 d .
  • Linear portions 134 a - 134 d each arranged to incline by a prescribed angle to allow the working fluid condensed and thus liquefied in linear portions 134 a - 134 d to be pulled by gravity to return through the inclined linear portions 134 a - 134 c toward header pipe 132 , can prevent aligned pipe 133 from having the working fluid staying therein.
  • Linear portions 134 a - 134 d thud previously arranged to incline relative to bottom surface 301 of casing 300 by a prescribed angle allows the working fluid to smoothly flow regardless of how casing 300 is disposed, and as a result allow loop thermosyphon 100 F to reliably operate.
  • the present embodiment provides a loop thermosyphon 100 G also utilized as a heat transfer system associated with a heated portion of a Stirling refrigerating machine, similarly as described in the first to sixth embodiments. Accordingly, the components similar to those of the first to sixth embodiments are shown in the figures with identical reference characters.
  • the present embodiment provides loop thermosyphon 100 G including a condenser 130 G having header pipe 131 associated with a feed pipe and extending vertically, header pipe 132 associated with a return pipe and also extending vertically, and the plurality of aligned pipes 133 connecting header pipes 131 and 132 together.
  • the plurality of aligned pipes 133 are each a linearly extending pipe and a plurality of such linear tubes are vertically arranged in parallel layers to form condenser 130 G.
  • the plurality of aligned pipes 133 has a plurality of radiating fins 136 assembled thereto. Note that in condenser 130 G header pipe 131 extends in a direction orthogonal that in which each aligned pipe 133 extends and header pipe 132 extends in a direction orthogonal to that in which each aligned pipe 133 extends.
  • loop thermosyphon 100 G has condenser 130 G arranged to entirely incline relative to bottom surface 301 of casing 300 of equipment by an angle ⁇ 5 so that condenser 130 G has aligned pipes 133 each arranged to incline in a direction allowing the aligned pipe to have a smaller distance to bottom surface 301 of casing 300 of the equipment as the aligned pipe extends downstream (or extends from header pipe 131 toward header pipe 132 ).
  • Condenser 130 G previously, entirely inclined to allow the working fluid condensed and thus liquefied in aligned pipe 133 to be pulled by gravity to return through aligned pipe 133 toward header pipe 132 , can prevent aligned pipe 133 from having the working fluid staying therein.
  • the working fluid can smoothly flow regardless of how casing 300 is disposed, and as a result loop thermosyphon 100 F can reliably be operated.
  • the header pipes may be arranged to extend horizontally. If the header pipes are thus arranged, the header pipes will be connected by parallel or linear tubes arranged horizontally in parallel. In that case, the condenser is similarly arranged to entirely incline relative to a bottom surface of a casing of equipment by a prescribed angle so that the condenser has the aligned pipes each arranged to incline in a direction allowing the aligned pipe to have a smaller distance to the bottom surface as the aligned pipe extends downstream (or extends from the header pipe associated with the feed pipe toward that associated with the return pipe).
  • the loop thermosyphon can reliably operate.
  • header pipes associated with the feed and return pipes, respectively may not be connected by aligned pipes arranged in a single row.
  • the aligned pipes may be staggered in a direction traversing that in which the aligned pipes extend.
  • the present embodiment provides a loop thermosyphon 100 H also utilized as a heat transfer system associated with a heated portion of a Stirling refrigerating machine, similarly as described in the first to seventh embodiments. Accordingly, the components similar to those of the first to seventh embodiments are shown in the figures with identical reference characters.
  • the present embodiment provides loop thermosyphon 100 H including a condenser 130 H having header pipe 131 associated with a feed pipe and extending vertically, header pipe 132 associated with a return pipe and also extending vertically, and the plurality of aligned pipes 133 connecting header pipes 131 and 132 together.
  • the plurality of aligned pipes 133 are each a linearly extending pipe and a plurality of such linear tubes are vertically arranged in parallel layers to form condenser 130 H.
  • the plurality of aligned pipes 133 has a plurality of radiating fins 136 assembled thereto. Note that for loop thermosyphon 100 H header pipes 131 and 132 are arranged such that header pipes 131 and 132 extend in a direction overlapping a normal to bottom surface 301 of casing 300 of equipment.
  • loop thermosyphon 100 H has linear aligned pipes 133 arranged to entirely incline relative to bottom surface 301 by an angle ⁇ 6 so that condenser 130 G has aligned pipes 133 each arranged to incline in a direction allowing the aligned pipe to have a smaller distance to bottom surface 301 as the aligned pipe extends downstream (or extends from header pipe 131 toward header pipe 132 ).
  • Aligned pipe 133 previously inclined to allow the working fluid condensed and thus liquefied therein to be pulled by gravity to return therethrough toward header pipe. 132 , can be prevented from having the working fluid staying therein.
  • the working fluid can smoothly flow regardless of how casing 300 is disposed, and as a result loop thermosyphon 100 G can reliably be operated.
  • the header pipes may be arranged to extend horizontally. If the header pipes are thus arranged, the header pipes will be connected by parallel, linear tubes arranged horizontally in parallel.
  • the condenser is similarly arranged to entirely incline relative to a bottom surface of a casing of equipment by a prescribed angle so that the condenser has the aligned pipes each arranged to incline in a direction allowing the aligned pipe to have a smaller distance to the bottom surface as the aligned pipe extends downstream (or extends from the header pipe associated with the feed pipe toward that associated with the return pipe).
  • the loop thermosyphon can reliably operate.
  • header pipes associated with the feed and return pipes, respectively may not be connected by aligned pipes arranged in a single row.
  • the aligned pipes may be staggered in a direction traversing that in which the aligned pipes extend.
  • the present embodiment provides a Stirling refrigerator having the loop thermosyphon of any of the first to eighth embodiments as a heat transfer system associated with a heated portion of a Stirling refrigerating machine disposed in a casing.
  • the present embodiment provides a Stirling refrigerator 1000 including a freezer section 1028 and a chiller section 1029 as a refrigeration section.
  • Stirling refrigerator 1000 includes loop thermosyphon 100 as a heat transfer system associated with a heated portion to cool a heated portion 204 of a Stirling refrigerating machine 200 .
  • Stirling refrigerating machine 200 has a cold portion 206 generating cryogenic temperature utilized by a heat transfer system 1020 associated with the cold portion (indicated in FIG. 14 by a broken line) to cool the refrigerator's interior.
  • the heat transfer system associated with the cold portion may also be configured of a loop thermosyphon or may be a heat transfer system utilizing forced convection.
  • the heat transfer system associated with the heated portion, or loop thermosyphon 100 includes evaporator 110 attached to surround and thus contact heated portion 204 of Stirling refrigerating machine 200 , and condenser 130 connected to evaporator 110 by a feed pipe and a return pipe.
  • Evaporator 110 , condenser 130 and feed and return pipes 120 and 140 form a circulation circuit having ethanol-added water or the like sealed therein as a coolant.
  • condenser 130 is arranged to be upper (or higher) than evaporator 110 .
  • Stirling refrigerating machine 200 is arranged in Stirling refrigerator 1000 at a rear, upper portion. Furthermore, heat transfer system 1020 associated with the cold portion is arranged in Stirling refrigerator 1000 closer to the rear side. In contrast, the heat transfer system associated with the heated portion, or loop thermosyphon 100 , is arranged in Stirling refrigerator 1000 at an upper portion. Note that thermosyphon 100 has condenser 130 provided in a duct 1024 provided in Stirling refrigerator 1000 at an upper portion.
  • Stirling refrigerating machine 200 When Stirling refrigerating machine 200 is operated, heated portion 204 generates heat, which is thermally exchanged via condenser 130 of thermosyphon 100 with air present in duct 1024 .
  • An air blowing fan 1025 exhausts warm air present in duct 1024 to outside Stirling refrigerator 100 and also introduces air external to Stirling refrigerator 1000 to help to exchange heat.
  • cold portion 206 In contrast, cold portion 206 generates cryogenic temperature, which is thermally exchanged with an air stream present in cold duct 1023 , as indicated in FIG. 14 by an arrow.
  • a fan 1026 associated with a freezer section and a fan 1027 associated with a chiller section blow cooled, cold air toward freezer section 1028 and chiller section 1029 , respectively.
  • Each refrigeration section 1028 , 1029 provides a warm air stream which is again introduced into cold duct 1023 and repeatedly cooled.
  • loop thermosyphon 100 mounted in Stirling refrigerator 1000 as described above is any of loop thermosyphons 100 A- 100 H described in the first to eighth embodiments, it can reliably operate regardless of how Stirling refrigerator 100 has a casing disposed.
  • Stirling refrigerating machine 200 can be operated significantly efficiently and Stirling refrigerator 1000 can also be improved in performance.
  • the present embodiment provides a cooling apparatus having a major portion common in structure to that of the second conventional example described hereinbefore. Accordingly, components identical to those of the cooling apparatus of the second conventional example are identically labeled.
  • the present embodiment provides a cooling apparatus having condensate coolant pipe 11 having vertical pipes 11 A and 11 B with their respective upper ends connected to a lateral pipe 11 C at one and the other ends, respectively, and their respective lower ends connected to semi-rings 6 A and 6 B at their respective outer circumferential upper ends, respectively, similarly as has been done in the second conventional example.
  • vertical pipes 11 A and 11 B are connected at upper and lower ports that do not match as seen horizontally.
  • vertical pipes 11 A and 11 B are implemented by bent pipes having inclined portions 11 Aa and 11 Ba having a downward gradient (see FIG. 16A ). If cooling apparatus 50 (see FIG.
  • lateral pipe 11 C will have one of the ends lowest in level of the entirety of lateral pipe 11 C.
  • the coolant's condensate will flow through the vertical pipe having a lower inlet and thus be prevented from staying in lateral pipe 11 C.
  • refrigerators are to be installed at places having an inclination of at most 5° including no inclination. Accordingly by setting at least 5° for a downward gradient ⁇ of inclined portions 11 Aa and 11 Ba of the vertical pipes with reference to cooling apparatus 500 placed with no inclination (see FIG. 16A ), the vertical pipes can have inclined portions 11 Aa and 11 Ba with the downward gradient maintained if cooling apparatus 50 is inclined by 5°, and the thermosyphon can be prevented from failing to function. Thus the coolant can reliably be circulated.
  • vapor coolant pipe 11 has lateral pipe 11 C with a degassing charge pipe 21 attached thereto. If the heat transfer cycle associated with the heated portion is operated with water used as a coolant, an uncondensed gas (or air) solved and thus present in water needs to be removed. Accordingly, after the water or coolant is shielded charge pipe 21 is used to vacuum a shielded system internal to the cycle. Charge pipe 21 attached at a location high in level can prevent water from being sucked in vacuuming the shielded system and can also improve efficiency in vacuuming the system.
  • the first to tenth embodiments have been described by exemplifying a loop thermosyphon employed in a heat transfer system associated with a heated portion of a Stirling refrigerating machine, the present invention is as a matter of course also applicable to other devices having a heat source.

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  • 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)
US10/570,132 2003-09-02 2004-08-12 Loop type thermo siphon, stirling cooling chamber, and cooling apparatus Abandoned US20070028626A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2003-309708 2003-09-02
JP2003309708A JP2005077018A (ja) 2003-09-02 2003-09-02 ループ型サーモサイフォンおよびスターリング冷却庫ならびにループ型サーモサイフォンの組付け構造
JP2004-020679 2004-01-29
JP2004020679A JP3689761B2 (ja) 2004-01-29 2004-01-29 冷却装置
PCT/JP2004/011600 WO2005024331A1 (fr) 2003-09-02 2004-08-12 Thermosiphon du type boucle, chambre de refroidissement a cycle stirling et appareil de refroidissement

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EP (1) EP1669710A1 (fr)
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US20110173978A1 (en) * 2010-01-21 2011-07-21 The Abell Foundation, Inc. Ocean Thermal Energy Conversion Cold Water Pipe
US20120011849A1 (en) * 2010-01-21 2012-01-19 Cole Barry R Ocean Thermal Energy Conversion Power Plant
US20120131932A1 (en) * 2000-06-30 2012-05-31 Alliant Techsystems Inc. Heat transfer system
US20130019623A1 (en) * 2011-07-21 2013-01-24 Jo Ilhyeon Refrigerator
US20130160476A1 (en) * 2011-12-21 2013-06-27 Sangbong Lee Refrigerator
US20130284414A1 (en) * 2012-04-26 2013-10-31 Lg Electronics Inc. Heat exchanger
WO2013167468A1 (fr) * 2012-05-08 2013-11-14 Inficon Gmbh Dispositif de prélèvement d'un fluide
US20140003068A1 (en) * 2012-06-27 2014-01-02 Flextronics Ap, Llc Cooling system for led device
US20140116653A1 (en) * 2012-10-25 2014-05-01 Cooling House Co., Ltd. Loop thermosyphon cooling device
US8893513B2 (en) 2012-05-07 2014-11-25 Phononic Device, Inc. Thermoelectric heat exchanger component including protective heat spreading lid and optimal thermal interface resistance
US20150016123A1 (en) * 2012-06-27 2015-01-15 Flextronics Ap, Llc Automotive led headlight cooling system
US8991194B2 (en) 2012-05-07 2015-03-31 Phononic Devices, Inc. Parallel thermoelectric heat exchange systems
US9117991B1 (en) 2012-02-10 2015-08-25 Flextronics Ap, Llc Use of flexible circuits incorporating a heat spreading layer and the rigidizing specific areas within such a construction by creating stiffening structures within said circuits by either folding, bending, forming or combinations thereof
US9273887B2 (en) 2000-06-30 2016-03-01 Orbital Atk, Inc. Evaporators for heat transfer systems
US9593871B2 (en) 2014-07-21 2017-03-14 Phononic Devices, Inc. Systems and methods for operating a thermoelectric module to increase efficiency
US9618185B2 (en) 2012-03-08 2017-04-11 Flextronics Ap, Llc LED array for replacing flourescent tubes
US9748460B2 (en) 2013-02-28 2017-08-29 Flextronics Ap, Llc LED back end assembly and method of manufacturing
US9909571B2 (en) 2011-08-15 2018-03-06 The Abell Foundation, Inc. Ocean thermal energy conversion power plant cold water pipe connection
US10043596B2 (en) 2014-02-27 2018-08-07 Korea Atomic Energy Research Institute Water-air combined passive feed water cooling apparatus and system
US10156385B1 (en) 2017-08-15 2018-12-18 Christopher Kapsha Multistage refrigeration system
US20190074116A1 (en) * 2013-04-24 2019-03-07 Siemens Plc Assembly comprising a two-stage cryogenic refrigerator and associated mounting arrangement
US10274221B1 (en) 2017-12-22 2019-04-30 Mitek Holdings, Inc. Heat exchanger
US10458683B2 (en) 2014-07-21 2019-10-29 Phononic, Inc. Systems and methods for mitigating heat rejection limitations of a thermoelectric module
US10619944B2 (en) 2012-10-16 2020-04-14 The Abell Foundation, Inc. Heat exchanger including manifold
WO2019152913A3 (fr) * 2018-02-04 2020-05-07 Tiwari Ratnesh Système de refroidissement d'eau
CN112066581A (zh) * 2020-09-21 2020-12-11 珠海格力电器股份有限公司 一种制冷系统、方法及制冷设备
CN112985132A (zh) * 2021-03-05 2021-06-18 太原理工大学 一种斯特林发电及强制对流散热的重力热管装置
US20210262721A1 (en) * 2019-07-22 2021-08-26 Mayekawa Mfg. Co., Ltd. Defrost system
US20210341230A1 (en) * 2018-09-25 2021-11-04 Hughes Safety Showers Limited Passive water cooler

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WO2008034185A1 (fr) * 2006-09-21 2008-03-27 Rheem Australia Pty Limited Échangeur de chaleur incliné
US9552025B2 (en) 2014-09-23 2017-01-24 Google Inc. Cooling electronic devices in a data center
US10448543B2 (en) 2015-05-04 2019-10-15 Google Llc Cooling electronic devices in a data center
US10462935B2 (en) 2015-06-23 2019-10-29 Google Llc Cooling electronic devices in a data center
US10349561B2 (en) 2016-04-15 2019-07-09 Google Llc Cooling electronic devices in a data center

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US7013954B2 (en) * 2002-01-23 2006-03-21 Twinbird Corporation Thermosiphon
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Cited By (51)

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US20120131932A1 (en) * 2000-06-30 2012-05-31 Alliant Techsystems Inc. Heat transfer system
US9631874B2 (en) * 2000-06-30 2017-04-25 Orbital Atk, Inc. Thermodynamic system including a heat transfer system having an evaporator and a condenser
US9273887B2 (en) 2000-06-30 2016-03-01 Orbital Atk, Inc. Evaporators for heat transfer systems
US20110173979A1 (en) * 2010-01-21 2011-07-21 The Abell Foundation, Inc. Ocean Thermal Energy Conversion Plant
US10184457B2 (en) 2010-01-21 2019-01-22 The Abell Foundation, Inc. Ocean thermal energy conversion plant
US9797386B2 (en) * 2010-01-21 2017-10-24 The Abell Foundation, Inc. Ocean thermal energy conversion power plant
US20110173978A1 (en) * 2010-01-21 2011-07-21 The Abell Foundation, Inc. Ocean Thermal Energy Conversion Cold Water Pipe
US9086057B2 (en) 2010-01-21 2015-07-21 The Abell Foundation, Inc. Ocean thermal energy conversion cold water pipe
US11859597B2 (en) 2010-01-21 2024-01-02 The Abell Foundation, Inc. Ocean thermal energy conversion power plant
US11371490B2 (en) 2010-01-21 2022-06-28 The Abell Foundation, Inc. Ocean thermal energy conversion power plant
US20120011849A1 (en) * 2010-01-21 2012-01-19 Cole Barry R Ocean Thermal Energy Conversion Power Plant
US8899043B2 (en) 2010-01-21 2014-12-02 The Abell Foundation, Inc. Ocean thermal energy conversion plant
US10844848B2 (en) 2010-01-21 2020-11-24 The Abell Foundation, Inc. Ocean thermal energy conversion power plant
US9618254B2 (en) * 2011-07-21 2017-04-11 Lg Electronics Inc. Refrigerator
US20130019623A1 (en) * 2011-07-21 2013-01-24 Jo Ilhyeon Refrigerator
US9909571B2 (en) 2011-08-15 2018-03-06 The Abell Foundation, Inc. Ocean thermal energy conversion power plant cold water pipe connection
US20130160476A1 (en) * 2011-12-21 2013-06-27 Sangbong Lee Refrigerator
US9239182B2 (en) * 2011-12-21 2016-01-19 Lg Electronics Inc. Refrigerator
US9117991B1 (en) 2012-02-10 2015-08-25 Flextronics Ap, Llc Use of flexible circuits incorporating a heat spreading layer and the rigidizing specific areas within such a construction by creating stiffening structures within said circuits by either folding, bending, forming or combinations thereof
US9618185B2 (en) 2012-03-08 2017-04-11 Flextronics Ap, Llc LED array for replacing flourescent tubes
US20130284414A1 (en) * 2012-04-26 2013-10-31 Lg Electronics Inc. Heat exchanger
US9353997B2 (en) * 2012-04-26 2016-05-31 Lg Electronics Inc. Heat exchanger
US8893513B2 (en) 2012-05-07 2014-11-25 Phononic Device, Inc. Thermoelectric heat exchanger component including protective heat spreading lid and optimal thermal interface resistance
US10012417B2 (en) 2012-05-07 2018-07-03 Phononic, Inc. Thermoelectric refrigeration system control scheme for high efficiency performance
US9103572B2 (en) 2012-05-07 2015-08-11 Phononic Devices, Inc. Physically separated hot side and cold side heat sinks in a thermoelectric refrigeration system
US8991194B2 (en) 2012-05-07 2015-03-31 Phononic Devices, Inc. Parallel thermoelectric heat exchange systems
US9341394B2 (en) 2012-05-07 2016-05-17 Phononic Devices, Inc. Thermoelectric heat exchange system comprising cascaded cold side heat sinks
US9234682B2 (en) 2012-05-07 2016-01-12 Phononic Devices, Inc. Two-phase heat exchanger mounting
US9310111B2 (en) 2012-05-07 2016-04-12 Phononic Devices, Inc. Systems and methods to mitigate heat leak back in a thermoelectric refrigeration system
RU2638701C2 (ru) * 2012-05-08 2017-12-15 Инфикон Гмбх Устройство для отбора сжатой текучей среды из холодильной установки
US10365024B2 (en) 2012-05-08 2019-07-30 Inficon Gmbh Removal device for a fluid
WO2013167468A1 (fr) * 2012-05-08 2013-11-14 Inficon Gmbh Dispositif de prélèvement d'un fluide
US9366394B2 (en) * 2012-06-27 2016-06-14 Flextronics Ap, Llc Automotive LED headlight cooling system
US9356214B2 (en) * 2012-06-27 2016-05-31 Flextronics Ap, Llc. Cooling system for LED device
US20140003068A1 (en) * 2012-06-27 2014-01-02 Flextronics Ap, Llc Cooling system for led device
US20150016123A1 (en) * 2012-06-27 2015-01-15 Flextronics Ap, Llc Automotive led headlight cooling system
US10619944B2 (en) 2012-10-16 2020-04-14 The Abell Foundation, Inc. Heat exchanger including manifold
US20140116653A1 (en) * 2012-10-25 2014-05-01 Cooling House Co., Ltd. Loop thermosyphon cooling device
US9748460B2 (en) 2013-02-28 2017-08-29 Flextronics Ap, Llc LED back end assembly and method of manufacturing
US20190074116A1 (en) * 2013-04-24 2019-03-07 Siemens Plc Assembly comprising a two-stage cryogenic refrigerator and associated mounting arrangement
US10043596B2 (en) 2014-02-27 2018-08-07 Korea Atomic Energy Research Institute Water-air combined passive feed water cooling apparatus and system
US10458683B2 (en) 2014-07-21 2019-10-29 Phononic, Inc. Systems and methods for mitigating heat rejection limitations of a thermoelectric module
US9593871B2 (en) 2014-07-21 2017-03-14 Phononic Devices, Inc. Systems and methods for operating a thermoelectric module to increase efficiency
US10156385B1 (en) 2017-08-15 2018-12-18 Christopher Kapsha Multistage refrigeration system
US10274221B1 (en) 2017-12-22 2019-04-30 Mitek Holdings, Inc. Heat exchanger
WO2019152913A3 (fr) * 2018-02-04 2020-05-07 Tiwari Ratnesh Système de refroidissement d'eau
US11802738B2 (en) 2018-02-04 2023-10-31 Ratnesh Tiwari Water cooling system
US20210341230A1 (en) * 2018-09-25 2021-11-04 Hughes Safety Showers Limited Passive water cooler
US20210262721A1 (en) * 2019-07-22 2021-08-26 Mayekawa Mfg. Co., Ltd. Defrost system
CN112066581A (zh) * 2020-09-21 2020-12-11 珠海格力电器股份有限公司 一种制冷系统、方法及制冷设备
CN112985132A (zh) * 2021-03-05 2021-06-18 太原理工大学 一种斯特林发电及强制对流散热的重力热管装置

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KR100746795B1 (ko) 2007-08-06

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