US3857441A - Heat pipe wick restrainer - Google Patents

Heat pipe wick restrainer Download PDF

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US3857441A
US3857441A US00017106A US1710670A US3857441A US 3857441 A US3857441 A US 3857441A US 00017106 A US00017106 A US 00017106A US 1710670 A US1710670 A US 1710670A US 3857441 A US3857441 A US 3857441A
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wick
heat pipe
restrainer
evaporator
tubular
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US00017106A
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F Arcella
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CBS Corp
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Westinghouse Electric Corp
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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
    • F28D15/04—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 tubes having a capillary structure
    • F28D15/046—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 tubes having a capillary structure characterised by the material or the construction of the capillary structure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49353—Heat pipe device making

Definitions

  • heat pipe wicks are manufactured by various methods such as by fabricating channels into the heat pipe walls by a broaching process.
  • the channels which permit unrestricted fluid flow from the heat pipe condenser to the evaporator section, are covered by fine mesh screen to establish greater capillary wicking forces.
  • Composite wicks have also been manufactured by placing layers of heavy mesh screen (30 to 60 mesh) beneath the wick- /vapor interface layers of fine mesh screen (200 to 400 mesh).
  • Another technique comprises the fabrication of open annulus wicks by swaging several turns of screen wound between two copper tubes. The copper tubes are then etched away and the porous rigid wick is sinter bonded. Upon insertion into a heat pipe with an open annulus between the wick and heat pipe walls, this wick presents an optimum arrangement for liquid metal charged heat pipes.
  • the wick support structure In order to maintain optimum heat pipe operation the wick support structure must also be able to prevent fluid loses at the vapor-fluid interface caused by the high velocity vapors traveling between the evaporator and condenser sections (entrainment). None of the aforementioned techniques have been able to cope with this problem and the result has been to starve the evaporator region of the heat pipe.
  • this invention overcomes the difficulties experienced by the prior art by utilizing a tubular heat pipe Wick restrainer which comprises a tubular member with an outside diameter approximately equal to the desired inside diameter of the wick structure.
  • the tubular member has circumferentially placed holes which permit the heat pipe working fluid to evaporate and condense at the evaporator and condenser sections respectively.
  • the resulting restrainer is both porous and retains good circumferential strength. This circumferential rigidity permits uniform pressure to be exerted on the wick structure.
  • the wick structure is tightly rolled onto the restrainer tube, possibly tack welded to it, and inserted into the heat pipe tube.
  • a tight fit can be employed, or a sliding fit can be used if the wick assembly is to be swaged.
  • the restrainer tube (1) uniformly presses the wick onto the heat pipe inner walls; (2) permits easier heat pipe assembly and processing; and (3) presents a non-homogeneous surface at the liquid/vapor interface to break up the vapor flow path along the wick liquid/- vapor interface. This last property prevents the rapid vapor flow from pulling fluid out of the wick (entrainment) and thus starving the evaporator region.
  • FIG. 1 is an isometric view of a heat pipe embodying the principles of this invention, having a portion thereof cut away for clarity;
  • FIG. 2 is an isometric view of the heat pipe of FIG. 1, broken away in layers, and is illustrative of the position of the restrainer tube with respect to the other elements of the heat pipe;
  • FIG. 3 is a development of a portion of the heat pipe wick restrainer tube of FIG. 2 and is illustrative of a hole pattern which may be utilized with this invention.
  • a heat pipe 10 constructed in accordance with the principles of this invention includes an evacuated chamber 12 whose inside walls are lined with a capillary structure, or wick 14, that is saturated with a volatile fluid.
  • a tubular support member, or restrainer 30, having an outside diameter approximately equal to the desired inside diameter of the wick structure 14, is positioned within the evacuated chamber 12 against the wick 114 which closely receives the support member 30 in the center thereof.
  • the support member 30 exerts uniform pressure on the inner surface of the wick 14 so as to restrain the wick 14 against the inner walls of the heat pipe 10.
  • the support member 30 has circumferentially placed holes 32, which allow the working fluid to evaporate and condense at the evaporator section 16 and condenser section 18 respectively.
  • Vapor heat transfer serves to transport the heat energy from the evaporator section 16 at one end of the pipe to the condenser section 18 at the other end.
  • Capillary action returns the condensed working fluid back to the evaporator section 16 to complete the cycle.
  • the working fluid absorbs heat at the evaporator section 16 and changes from its liquid state to a vapor state.
  • the amount of heat necessary to cause this change of state is the latent heat of vaporization.
  • the pressure at the evaporator section 16 increases.
  • the vapor pressure sets up a pressure differential between the ends of the heat pipe, and this pressure differential causes the vapor, and thus the heat energy, to move towards the condenser section 18.
  • the vapor arrives at the condenser section 18, it is subjected to a temperature lower than that of the evaporator section 16 and condenses, thereby releasing the thermal energy stored in its heat of vaporization at the condenser section 18 of the heat pipe. As the vapor condenses the pressure at the condenser section 18 decreases so that the necessary pressure differential for continued vapor heat flow is maintained. Movement of the fluid from the condenser section 18 back to the evaporator section 16 is accomplished by capillary action within the wick 14, which connects the condenser 18 to the evaporator 16.
  • the heat pipe wick 14 In order to provide optimum heat pipe operation the heat pipe wick 14 must maintain uniform contact with the inner walls of the heat pipe tube 20 and means must be provided for preventing fluid loses in the wick 14 at the wick/vapor interface, due to the high velocity vapor flow along this interface (sometimes approaching sonic velocities).
  • the heat pipe wick restrainer, or support 30, includes a tubular member 34 with an outside diameter approximately equal to the desired inside diameter of the heat pipe wick 14.
  • the tubular member 34 has circumferentially placed holes 32 which allow the heat pipe working fluid to evaporate and condense at the evaporator and condenser sections respectively.
  • the holes 32 are desirably arranged in a pattern, such as the hexagonal pattern illustrated in FIG. 3, and extend over the entire circumference of the restrainer. For closest packing, it is suggested that the outside diameter of the holes 32, should be approximately one-third the restrainer tube outside diameter.
  • the resulting restrainer is approximately 50 percent porous and retains good circumferential strength. This circumferential rigidity permits uniform pressure to be exerted on the wick structure 14.
  • the size of the holes and the hole pattern may vary depending upon the heat pipe wick structure and its intended use.
  • the holes may be positioned at the evaporator and condenser sections without extending over the entire length of the restrainer tube, and the size of the holes may vary with the wick'surface area required to produce the desired rate of vaporization and condensation of the working fluid.
  • tubular member 34 need not be of circular cylindrical configuration, but may be desirably designed to conform to any geometric shape the heat pipe wick may form. What has been shown and described is merely an exemplary embodiment of this invention and it is not intended to be limitative thereof.
  • the restrainer tube (1) uniformly presses the wick onto the heat pipe inner walls; (2) permits easier heat pipe assembly and (3) presents a nonhomogeneous surface to break up the vapor flow path along the wick liquid/vapor interface. This last property prevents the rapid vapor flow from pulling fluid out of the wick and thus starving the evaporator region.
  • a heat pipe comprising a sealed tubular outer casing, a tubular wick structure positioned in said outer casing and closely received by the inner surface thereof, and a tubular substantially nonresilient, wick restrainer position within said casing and closely received by the inner surface of said wick structure, said wick restrainer being formed to provide uniform support to said wick structure, to maintain the same in engagement with said inner surface of said outer casing.
  • wick restrainer has an outside diameter approximately equal to the desired inside diameter of the wick structure, said wick restrainer extending over the evaporator and condenser regions of the heat pipe and being perforated along the evaporator and condenser regions to allow the heat pipe working fluid respectively to evaporate at the wick/vapor interface of the evaporator section and condense at the wick/vapor interface of the condenser section.

Abstract

This invention relates in general to heat pipes and more particularly to a tubular heat pipe wick restrainer which includes a tubular member with an outside diameter equal to the desired inside diameter of the wick structure. The tubular member has circumferentially placed holes which allow the heat pipe working fluid to evaporate and condense at the evaporator and condenser sections respectively.

Description

llnited States Areella HEAT PIPE WHCK RESTRATNER OTHER PUBLICATIONS [75] Inventor: Frank Anemia Bethel Park Deverall, J. E. et al. High Thermal Conductances De- [73] Assignee: Westinghouse Electric Corporation, Vices, L08 AlamOS Scientific Laboratory 1 L05 Alamos, Pi b h P New Mexico (LA-3211), April, 1965 (Microfische),
. l a d 29. 22 Filed: Mar. 6, 1970 pgs [21] Appl. N0.: 17,106 Primary Examiner-Albert W. Davis, Jr.
Attorney, Agent, or FirmD. C. Abeles [52] 1.1.8. Cl. 165/105, 29/157.3 [51] 1111. C1. F2811 15/00 ABSTRAlCT of Search R invention slates in genera] to heat pipes and more particularly to a tubular heat pipe wick re- References Cited strainer which includes a tubular member with an out- UNITED STATES PATENTS side diameter equal to the desired inside diameter of 2,797,554 7/1957 Donovan 165/179 x the Wick Structure The tubular member has Circum- 3,414,475 12/1968 Fiebelmann 165/105 x e entially placed holes hich allow the heat pipe 3,429,122 2/1969 Prauda et al.. 165/105 X working fluid to evaporate and condense at the evapo- 3,498,369 3/1970 Le a 65/l rator and condenser sections respectively. 3,528,494 9/1970 Levedahl 165/105 3,554,183 1/1971 Grover et a1 165/105 x 7 Claims, 3 Drawing Figures 34 20 10 i H i j 1 T i p vvo'ovvv'ee'ee" \vk (O (O (O (0 1 14 1/ 1 Patented Dec. 31, 1974 3,857,441
(W41 w vvvvvvvvvvv m HM g FIG. 1'
FIG. 3
INVENTOR FRANK 0. ARCELLA ATTORNEY HEAT PIPE WICK RESTRAINER BACKGROUND OF THE INVENTION This invention pertains to heat pipes and more particularly to a new heat pipe wick support.
In accordance with the present state-of-the-art, heat pipe wicks are manufactured by various methods such as by fabricating channels into the heat pipe walls by a broaching process. The channels, which permit unrestricted fluid flow from the heat pipe condenser to the evaporator section, are covered by fine mesh screen to establish greater capillary wicking forces. Composite wicks have also been manufactured by placing layers of heavy mesh screen (30 to 60 mesh) beneath the wick- /vapor interface layers of fine mesh screen (200 to 400 mesh). Another technique comprises the fabrication of open annulus wicks by swaging several turns of screen wound between two copper tubes. The copper tubes are then etched away and the porous rigid wick is sinter bonded. Upon insertion into a heat pipe with an open annulus between the wick and heat pipe walls, this wick presents an optimum arrangement for liquid metal charged heat pipes.
While these fabrication techniques have yielded heat pipes which are both homogeneous in pore size and porosity and chemically compatible with the heat pipe working fluids, they have not provided wicks that maintain uniform contact with the heat pipe inner surfaces. Such uniform contact is a necessary pre-requisite for optimum heat pipe operation. Thus, retaining the wick against the heat pipe inner walls has been a problem. The prior art has employed several methods to correct this deficiency. One such method comprises threading a drawn helical spring through the wick material and releasing the spring so that the coils press the wick against the heat pipe inner walls. The problem with this method is that the spring provides non-uniform support over the wick surface area causing constrictions at the spring/wick interfaces which inhibit the capillary action of the wick. This method has particularly proved to be impractical in high temperature heat pipes where at elevated temperatures the spring loses its tension and sags, thereby releasing the wick from the heat pipe walls and creating gaps which result in hot spots, which may burn through the heat pipe walls. Another method employed has been to produce wicks by the aforementioned swaging process. The resulting wicks are tight, homogeneous, free standing, channeled structures. These wicks, however, can soften after a time at elevated temperatures and sag, or be pushed away from the walls by the working fluid. Other wicks have been fabricated by seam welding strips of wick material into tubes and inserting them into heat pipe tubes. Again no uniform restraining device presses the wick to the tube wall.
In order to maintain optimum heat pipe operation the wick support structure must also be able to prevent fluid loses at the vapor-fluid interface caused by the high velocity vapors traveling between the evaporator and condenser sections (entrainment). None of the aforementioned techniques have been able to cope with this problem and the result has been to starve the evaporator region of the heat pipe.
SUMMARY OF THE INVENTION Briefly, this invention overcomes the difficulties experienced by the prior art by utilizing a tubular heat pipe Wick restrainer which comprises a tubular member with an outside diameter approximately equal to the desired inside diameter of the wick structure. The tubular member has circumferentially placed holes which permit the heat pipe working fluid to evaporate and condense at the evaporator and condenser sections respectively. The resulting restrainer is both porous and retains good circumferential strength. This circumferential rigidity permits uniform pressure to be exerted on the wick structure.
The wick structure is tightly rolled onto the restrainer tube, possibly tack welded to it, and inserted into the heat pipe tube. A tight fit can be employed, or a sliding fit can be used if the wick assembly is to be swaged. Thus the restrainer tube: (1) uniformly presses the wick onto the heat pipe inner walls; (2) permits easier heat pipe assembly and processing; and (3) presents a non-homogeneous surface at the liquid/vapor interface to break up the vapor flow path along the wick liquid/- vapor interface. This last property prevents the rapid vapor flow from pulling fluid out of the wick (entrainment) and thus starving the evaporator region.
BRIEF DESCRIPTION OF THE DRAWINGS For a better understanding of an. exemplary embodiment of this invention, reference may be had to the accompanying drawings, in which:
FIG. 1 is an isometric view of a heat pipe embodying the principles of this invention, having a portion thereof cut away for clarity;
FIG. 2 is an isometric view of the heat pipe of FIG. 1, broken away in layers, and is illustrative of the position of the restrainer tube with respect to the other elements of the heat pipe; and
FIG. 3 is a development of a portion of the heat pipe wick restrainer tube of FIG. 2 and is illustrative of a hole pattern which may be utilized with this invention.
DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to the heat pipe illustrated in FIGS. 1 and 2, it will be appreciated that a heat pipe 10 constructed in accordance with the principles of this invention includes an evacuated chamber 12 whose inside walls are lined with a capillary structure, or wick 14, that is saturated with a volatile fluid. A tubular support member, or restrainer 30, having an outside diameter approximately equal to the desired inside diameter of the wick structure 14, is positioned within the evacuated chamber 12 against the wick 114 which closely receives the support member 30 in the center thereof. The support member 30 exerts uniform pressure on the inner surface of the wick 14 so as to restrain the wick 14 against the inner walls of the heat pipe 10. The support member 30 has circumferentially placed holes 32, which allow the working fluid to evaporate and condense at the evaporator section 16 and condenser section 18 respectively.
The operation of the heat pipe combines two familiar principles of physics; vapor heat transfer and capillary action. Vapor heat transfer serves to transport the heat energy from the evaporator section 16 at one end of the pipe to the condenser section 18 at the other end. Capillary action returns the condensed working fluid back to the evaporator section 16 to complete the cycle.
The working fluid absorbs heat at the evaporator section 16 and changes from its liquid state to a vapor state. The amount of heat necessary to cause this change of state is the latent heat of vaporization. As the working fluid vaporizes, the pressure at the evaporator section 16 increases. The vapor pressure sets up a pressure differential between the ends of the heat pipe, and this pressure differential causes the vapor, and thus the heat energy, to move towards the condenser section 18.
When the vapor arrives at the condenser section 18, it is subjected to a temperature lower than that of the evaporator section 16 and condenses, thereby releasing the thermal energy stored in its heat of vaporization at the condenser section 18 of the heat pipe. As the vapor condenses the pressure at the condenser section 18 decreases so that the necessary pressure differential for continued vapor heat flow is maintained. Movement of the fluid from the condenser section 18 back to the evaporator section 16 is accomplished by capillary action within the wick 14, which connects the condenser 18 to the evaporator 16.
In order to provide optimum heat pipe operation the heat pipe wick 14 must maintain uniform contact with the inner walls of the heat pipe tube 20 and means must be provided for preventing fluid loses in the wick 14 at the wick/vapor interface, due to the high velocity vapor flow along this interface (sometimes approaching sonic velocities).
This invention maintains the aforementioned criteria by utilizing the heat pipe wick restrainer 30, illustrated in H0. 2. The heat pipe wick restrainer, or support 30, includes a tubular member 34 with an outside diameter approximately equal to the desired inside diameter of the heat pipe wick 14. The tubular member 34 has circumferentially placed holes 32 which allow the heat pipe working fluid to evaporate and condense at the evaporator and condenser sections respectively. The holes 32 are desirably arranged in a pattern, such as the hexagonal pattern illustrated in FIG. 3, and extend over the entire circumference of the restrainer. For closest packing, it is suggested that the outside diameter of the holes 32, should be approximately one-third the restrainer tube outside diameter. The resulting restrainer is approximately 50 percent porous and retains good circumferential strength. This circumferential rigidity permits uniform pressure to be exerted on the wick structure 14.
It is to be understood that the size of the holes and the hole pattern may vary depending upon the heat pipe wick structure and its intended use. For example, the holes may be positioned at the evaporator and condenser sections without extending over the entire length of the restrainer tube, and the size of the holes may vary with the wick'surface area required to produce the desired rate of vaporization and condensation of the working fluid.
It is also to be understood that the tubular member 34 need not be of circular cylindrical configuration, but may be desirably designed to conform to any geometric shape the heat pipe wick may form. What has been shown and described is merely an exemplary embodiment of this invention and it is not intended to be limitative thereof.
Thus the restrainer tube: (1) uniformly presses the wick onto the heat pipe inner walls; (2) permits easier heat pipe assembly and (3) presents a nonhomogeneous surface to break up the vapor flow path along the wick liquid/vapor interface. This last property prevents the rapid vapor flow from pulling fluid out of the wick and thus starving the evaporator region.
I claim as my invention:
1. A heat pipe comprising a sealed tubular outer casing, a tubular wick structure positioned in said outer casing and closely received by the inner surface thereof, and a tubular substantially nonresilient, wick restrainer position within said casing and closely received by the inner surface of said wick structure, said wick restrainer being formed to provide uniform support to said wick structure, to maintain the same in engagement with said inner surface of said outer casing.
2. The heat pipe of claim 1 wherein said wick restrainer has an outside diameter approximately equal to the desired inside diameter of the wick structure, said wick restrainer extending over the evaporator and condenser regions of the heat pipe and being perforated along the evaporator and condenser regions to allow the heat pipe working fluid respectively to evaporate at the wick/vapor interface of the evaporator section and condense at the wick/vapor interface of the condenser section.
3. The heat pipe of claim 2 wherein said perforation in said wick restrainer has a diameter approximately equal to one-third of the outside diameter of said wick restrainer.
4. The heat pipe of claim 2 wherein the perforations in said wick restrainer are arranged in a hexagonal pattern.
5. The heat pipe of claim 2 wherein the perforations are arranged in a pattern extending over the entire surface of said wick restrainer.
6. The heat pipe of claim 1 wherein said wick restrainer is rigid.
7. The heat pipe of claim 1 wherein said tubular wick structure comprises wire mesh screen.

Claims (7)

1. A heat pipe comprising a sealed tubular outer casing, a tubular wick structure positioned in said outer casing and closely received by the inner surface thereof, and a tubular substantially nonresilient, wick restrainer position within said casing and closely received by the inner surface of said wick structure, said wick restrainer being formed to provide uniform support to said wick structure, to maintain the same in engagement with said inner surface of said outer casing.
2. The heat pipe of claim 1 wherein said wick restrainer has an outside diameter approximaTely equal to the desired inside diameter of the wick structure, said wick restrainer extending over the evaporator and condenser regions of the heat pipe and being perforated along the evaporator and condenser regions to allow the heat pipe working fluid respectively to evaporate at the wick/vapor interface of the evaporator section and condense at the wick/vapor interface of the condenser section.
3. The heat pipe of claim 2 wherein said perforation in said wick restrainer has a diameter approximately equal to one-third of the outside diameter of said wick restrainer.
4. The heat pipe of claim 2 wherein the perforations in said wick restrainer are arranged in a hexagonal pattern.
5. The heat pipe of claim 2 wherein the perforations are arranged in a pattern extending over the entire surface of said wick restrainer.
6. The heat pipe of claim 1 wherein said wick restrainer is rigid.
7. The heat pipe of claim 1 wherein said tubular wick structure comprises wire mesh screen.
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Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4018269A (en) * 1973-09-12 1977-04-19 Suzuki Metal Industrial Co., Ltd. Heat pipes, process and apparatus for manufacturing same
US4565243A (en) * 1982-11-24 1986-01-21 Thermacore, Inc. Hybrid heat pipe
EP0210337A2 (en) * 1985-07-25 1987-02-04 Dornier Gmbh Capillary-assisted evaporator
US6330907B1 (en) * 1997-03-07 2001-12-18 Mitsubishi Denki Kabushiki Kaisha Evaporator and loop-type heat pipe using the same
US6466442B2 (en) * 2001-01-29 2002-10-15 Ching-Bin Lin Guidably-recirculated heat dissipating means for cooling central processing unit
US20030159809A1 (en) * 2002-02-26 2003-08-28 Mikros Manufacturing, Inc. Capillary evaporator
US20030183372A1 (en) * 2002-03-29 2003-10-02 Cheng-Tien Lai Heat pipe incorporating outer and inner pipes
US6648063B1 (en) * 2000-04-12 2003-11-18 Sandia Corporation Heat pipe wick with structural enhancement
US20050051305A1 (en) * 2002-12-06 2005-03-10 Hsu Hul Chun Heat pipe
US20050230085A1 (en) * 2002-02-26 2005-10-20 Mikros Manufacturing, Inc. Capillary condenser/evaporator
US20050247435A1 (en) * 2004-04-21 2005-11-10 Hul-Chun Hsu Wick structure of heat pipe
US20060011328A1 (en) * 2004-07-16 2006-01-19 Hsu Hul-Chun Wick structure of heat pipe
US20060157229A1 (en) * 2005-01-14 2006-07-20 Foxconn Technology Co., Ltd. Heat pipe
US20060162905A1 (en) * 2005-01-27 2006-07-27 Hul-Chun Hsu Heat pipe assembly
US20060201655A1 (en) * 2005-03-11 2006-09-14 Chu-Wan Hong Heat pipe suitable for application in electronic device with limited mounting space
US20060207749A1 (en) * 2005-03-18 2006-09-21 Jaffe Limited Multi-layer wick structure of heat pipe
US20070034357A1 (en) * 2005-08-12 2007-02-15 Chuen-Shu Hou Heat pipe and method of producing the same
US20070056710A1 (en) * 2003-09-30 2007-03-15 Ut Starcom Lorea Limited Apparatus for cooling communication equipment using heat pipe
US20080105405A1 (en) * 2006-11-03 2008-05-08 Hul-Chun Hsu Heat Pipe Multilayer Capillary Wick Support Structure
CN100498186C (en) * 2006-06-02 2009-06-10 富准精密工业(深圳)有限公司 Hot pipe
CN100533042C (en) * 2005-03-15 2009-08-26 富准精密工业(深圳)有限公司 Net like heat pipe and its manufacture method
US20100155031A1 (en) * 2008-12-22 2010-06-24 Furui Precise Component (Kunshan) Co., Ltd. Heat pipe and method of making the same
US20100155032A1 (en) * 2008-12-22 2010-06-24 Furui Precise Component (Kunshan) Co., Ltd. Heat pipe and method of making the same
US20100175856A1 (en) * 2009-01-12 2010-07-15 Meyer Iv George Anthony Vapor chamber with wick structure of different thickness and die for forming the same
US20140138059A1 (en) * 2012-11-20 2014-05-22 Lockheed Martin Corporation Heat pipe with axial wick
US20180051432A1 (en) * 2016-08-18 2018-02-22 Ian R. Cooke Snow and Ice Melting Device, System and Corresponding Methods
JP2019007725A (en) * 2017-06-23 2019-01-17 株式会社リコー Loop type heat pipe, cooling device, and electronic device

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2797554A (en) * 1954-01-06 1957-07-02 William J Donovan Heat exchanger in refrigeration system
US3414475A (en) * 1965-05-20 1968-12-03 Euratom Heat pipes
US3429122A (en) * 1966-11-07 1969-02-25 Martin Marietta Corp Heat pipe regenerator for gas turbine engines
US3498369A (en) * 1968-06-21 1970-03-03 Martin Marietta Corp Heat pipes with prefabricated grooved capillaries and method of making
US3528494A (en) * 1966-11-07 1970-09-15 Teledyne Inc Heat pipe for low thermal conductivity working fluids
US3554183A (en) * 1968-10-04 1971-01-12 Acf Ind Inc Heat pipe heating system for a railway tank car or the like

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2797554A (en) * 1954-01-06 1957-07-02 William J Donovan Heat exchanger in refrigeration system
US3414475A (en) * 1965-05-20 1968-12-03 Euratom Heat pipes
US3429122A (en) * 1966-11-07 1969-02-25 Martin Marietta Corp Heat pipe regenerator for gas turbine engines
US3528494A (en) * 1966-11-07 1970-09-15 Teledyne Inc Heat pipe for low thermal conductivity working fluids
US3498369A (en) * 1968-06-21 1970-03-03 Martin Marietta Corp Heat pipes with prefabricated grooved capillaries and method of making
US3554183A (en) * 1968-10-04 1971-01-12 Acf Ind Inc Heat pipe heating system for a railway tank car or the like

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Deverall, J. E. et al. High Thermal Conductances Devices, Los Alamos Scientific Laboratory, Los Alamos, New Mexico (LA 3211), April, 1965 (Microfische), pgs. 1 and 29. *

Cited By (47)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4018269A (en) * 1973-09-12 1977-04-19 Suzuki Metal Industrial Co., Ltd. Heat pipes, process and apparatus for manufacturing same
US4565243A (en) * 1982-11-24 1986-01-21 Thermacore, Inc. Hybrid heat pipe
EP0210337A2 (en) * 1985-07-25 1987-02-04 Dornier Gmbh Capillary-assisted evaporator
EP0210337A3 (en) * 1985-07-25 1989-09-06 Dornier Gmbh Capillary-assisted evaporator
US6330907B1 (en) * 1997-03-07 2001-12-18 Mitsubishi Denki Kabushiki Kaisha Evaporator and loop-type heat pipe using the same
US6648063B1 (en) * 2000-04-12 2003-11-18 Sandia Corporation Heat pipe wick with structural enhancement
US7124507B1 (en) * 2000-04-12 2006-10-24 Sandia Corporation Method of manufacturing a heat pipe wick with structural enhancement
US6466442B2 (en) * 2001-01-29 2002-10-15 Ching-Bin Lin Guidably-recirculated heat dissipating means for cooling central processing unit
US20030159809A1 (en) * 2002-02-26 2003-08-28 Mikros Manufacturing, Inc. Capillary evaporator
US6863117B2 (en) * 2002-02-26 2005-03-08 Mikros Manufacturing, Inc. Capillary evaporator
US20050230085A1 (en) * 2002-02-26 2005-10-20 Mikros Manufacturing, Inc. Capillary condenser/evaporator
US7775261B2 (en) 2002-02-26 2010-08-17 Mikros Manufacturing, Inc. Capillary condenser/evaporator
US20030183372A1 (en) * 2002-03-29 2003-10-02 Cheng-Tien Lai Heat pipe incorporating outer and inner pipes
US20060201656A1 (en) * 2002-03-29 2006-09-14 Hon Hai Precision Ind Co., Ltd. Heat pipe incorporating outer and inner pipes
US7484553B2 (en) * 2002-03-29 2009-02-03 Fu Zhun Precision Industry (Shen Zhen) Co., Ltd. Heat pipe incorporating outer and inner pipes
US7543630B2 (en) * 2002-03-29 2009-06-09 Fu Zhun Precision Industry (Shen Zhen) Co., Ltd. Heat pipe incorporating outer and inner pipes
US20050051305A1 (en) * 2002-12-06 2005-03-10 Hsu Hul Chun Heat pipe
US8047267B2 (en) * 2003-09-30 2011-11-01 Transpacific Sonic, Llc Apparatus for cooling communication equipment using heat pipe
US20070056710A1 (en) * 2003-09-30 2007-03-15 Ut Starcom Lorea Limited Apparatus for cooling communication equipment using heat pipe
US20050247435A1 (en) * 2004-04-21 2005-11-10 Hul-Chun Hsu Wick structure of heat pipe
US6997244B2 (en) * 2004-07-16 2006-02-14 Hsu Hul-Chun Wick structure of heat pipe
US20060011328A1 (en) * 2004-07-16 2006-01-19 Hsu Hul-Chun Wick structure of heat pipe
US20060157229A1 (en) * 2005-01-14 2006-07-20 Foxconn Technology Co., Ltd. Heat pipe
US20060162905A1 (en) * 2005-01-27 2006-07-27 Hul-Chun Hsu Heat pipe assembly
US7159647B2 (en) * 2005-01-27 2007-01-09 Hul-Chun Hsu Heat pipe assembly
WO2006107492A3 (en) * 2005-03-08 2006-11-30 Mikros Mfg Inc Capillary condenser/evaporator
WO2006107492A2 (en) * 2005-03-08 2006-10-12 Mikros Manufacturing, Inc. Capillary condenser/evaporator
US20060201655A1 (en) * 2005-03-11 2006-09-14 Chu-Wan Hong Heat pipe suitable for application in electronic device with limited mounting space
CN100533042C (en) * 2005-03-15 2009-08-26 富准精密工业(深圳)有限公司 Net like heat pipe and its manufacture method
US20060207749A1 (en) * 2005-03-18 2006-09-21 Jaffe Limited Multi-layer wick structure of heat pipe
CN100437006C (en) * 2005-08-12 2008-11-26 富准精密工业(深圳)有限公司 Heat pipe and manufacturing method thereof
US7472479B2 (en) 2005-08-12 2009-01-06 Foxconn Technology Co., Ltd. Heat pipe and method of producing the same
US20070034357A1 (en) * 2005-08-12 2007-02-15 Chuen-Shu Hou Heat pipe and method of producing the same
CN100498186C (en) * 2006-06-02 2009-06-10 富准精密工业(深圳)有限公司 Hot pipe
US20080105405A1 (en) * 2006-11-03 2008-05-08 Hul-Chun Hsu Heat Pipe Multilayer Capillary Wick Support Structure
US20100155032A1 (en) * 2008-12-22 2010-06-24 Furui Precise Component (Kunshan) Co., Ltd. Heat pipe and method of making the same
US20100155031A1 (en) * 2008-12-22 2010-06-24 Furui Precise Component (Kunshan) Co., Ltd. Heat pipe and method of making the same
US8622117B2 (en) * 2008-12-22 2014-01-07 Furui Precise Component (Kunshan) Co., Ltd. Heat pipe including a main wick structure and at least one auxiliary wick structure
US20100175856A1 (en) * 2009-01-12 2010-07-15 Meyer Iv George Anthony Vapor chamber with wick structure of different thickness and die for forming the same
US9315280B2 (en) * 2012-11-20 2016-04-19 Lockheed Martin Corporation Heat pipe with axial wick
US20140138059A1 (en) * 2012-11-20 2014-05-22 Lockheed Martin Corporation Heat pipe with axial wick
US10538345B2 (en) 2012-11-20 2020-01-21 Lockheed Martin Corporation Heat pipe with axial wick
US11745901B2 (en) 2012-11-20 2023-09-05 Lockheed Martin Corporation Heat pipe with axial wick
US20180051432A1 (en) * 2016-08-18 2018-02-22 Ian R. Cooke Snow and Ice Melting Device, System and Corresponding Methods
US10988904B2 (en) * 2016-08-18 2021-04-27 Ian R. Cooke Snow and ice melting device, system and corresponding methods
JP2019007725A (en) * 2017-06-23 2019-01-17 株式会社リコー Loop type heat pipe, cooling device, and electronic device
US11371783B2 (en) * 2017-06-23 2022-06-28 Ricoh Company, Ltd. Loop heat pipe, cooling device, and electronic device

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