CN101055155A - Heat pipe - Google Patents
Heat pipe Download PDFInfo
- Publication number
- CN101055155A CN101055155A CNA2006100603042A CN200610060304A CN101055155A CN 101055155 A CN101055155 A CN 101055155A CN A2006100603042 A CNA2006100603042 A CN A2006100603042A CN 200610060304 A CN200610060304 A CN 200610060304A CN 101055155 A CN101055155 A CN 101055155A
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- China
- Prior art keywords
- heat
- cavity
- wall
- heat pipe
- section
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Classifications
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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
- F28D15/0275—Arrangements for coupling heat-pipes together or with other structures, e.g. with base blocks; Heat pipe cores
-
- 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
Abstract
The invention discloses a heat pipe which includes a sealed heat transmission cavity whose inner wall is equipped with capillary structure and in which appropriate working liquid is sealed. The heat transmission cavity can be divided into evaporation section, condensation section, thermal insulation section between the former two sections along the cavity length direction. The heat pipe also includes two sealed heat accumulation cavities which are respectively arranged on the outer wall of evaporation section and condensation section corresponding to the heat transmission cavity. The heat pipe promotes maximum radiation capacity for the heat pipe and reduces temperature difference between the evaporation section and the condensation section by larger heat absorption area and radiation area and latent heat of external part of the heat accumulation cavity.
Description
[technical field]
The present invention relates to a kind of heat conducting device, be meant a kind of heat pipe especially.
[background technology]
That heat pipe has is super-silent, flash heat transfer, high thermoconductivity, in light weight, characteristic such as size is little, no movable piece, simple in structure and multipurpose, and heat pipe can be played the part of the superconductor role of a large amount of heat energy of quick transmission and used widely under the situation that temperature almost remains unchanged; Its essential structure is in the capillary structure layer of airtight pipe material inner wall lining with easy absorption working fluid, its central space then is empty state, and in the airtight tubing that vacuumizes, inject the working fluid that is equivalent to capillary structure layer hole total measurement (volume), can be divided into evaporator section, condensation segment and adiabatic section therebetween according to the relevant position that absorbs with the heat that sheds; Its operation principle is that the liquid by working fluid, the latent heat of vapour two phase change transmit heat: be included in evaporator section and borrow evaporation latent heat to take away a large amount of heats from thermal source, make the working fluid evaporation and make steam fast by space in the pipe, arriving the condensation segment cooling condenses into liquid and discharges heat energy, above-mentioned working fluid then is back to evaporator section by the capillary force that capillary structure layer provided that is affixed on inside pipe wall, and the heat energy that reaches lasting phase change circulates and transmits heat.
Be applied at present in the heat radiation field of computer microprocessor (CPU), existing many use heat pipes are disclosed in the patent documentation in the heat abstractor of different structure and pattern, most typical example is to utilize heater element and be furnished with thermo-contact between the radiating fin base of fan, and the collocation heat pipe uses to increase the device of heat-transfer effect, but the available heat transfer area that is limited by high heater element is little, and the heat pipe quantity (total heat transfer) that can arrange in pairs or groups is restricted; In addition, be the heat demand of separating in response to higher heat flux (heat flux), between heater element and radiating fin base, often need install a soaking plate (spreader) with good heat conductivity additional, this soaking plate heat biography area than heater element usually is big, so that heat is passed to the load that evenly reduces high heater element heat flux before the radiating fin base earlier, shed by the heat pipe of bigger radiating fin collocation heat again high heat-generating electronic elements; For reaching above-mentioned purpose, soaking plate adopts the sheet metal of high coefficient of thermal conductivity such as copper, aluminium to make usually, but above-mentioned metallic plate still is limited by the limited heat conductivity of material itself, when being used in the heater element of high heat-flux, need bigger soaking plate area to come heat dispersing, so can produce tangible lateral distribution thermal resistance (spreading thermal resistance) and the effect of equal heat distribution is had a greatly reduced quality, cause the reduction of integral heat sink efficient; For promoting the effect of above-mentioned soaking plate, the proposition in existing steam-type heat radiation chamber (vapor chamber), it is to press close to the heat absorbing end vaporization of external heat source by contained a spot of working fluid in the capillary structure in the tabular hollow chamber, and heat is delivered to the radiating end condensation fast with the steam that produces, again by capillary force with condensate liquid be back to heat absorbing end vaporize next time/heat of condensation passes the function that circulative metabolism reaches heat radiation, but, directly influence the reliability of product because the volume production processing procedure of capillary structure (for example sintering or new micro-structural processing procedure) can't be kept close high heat transfer property energy in same batch product; And, its application is lacked flexibility because difform thermal source and radiator profile can't be satisfied in flat soaking plate or steam-type heat radiation chamber, and do good joining with the evaporator section and the condensation segment of heat pipe.
Because the performance test of heat pipe mainly focuses on maximum heat biography amount (Qmax) and by evaporator section two parameters of temperature difference (Δ T) to condensation segment, therefore under a given heat status transmission, can know its thermal resistance value by this temperature difference, and then the performance of assessment heat pipe; When given heat surpasses the maximum heat biography amount of heat pipe, owing to former normal heat transmission mechanism is destroyed thermal resistance value is increased suddenly, so that the temperature of evaporator section also rise sharply thereupon.
It is too small that existing heat pipe is subject to the endotherm area of evaporator section, with the heat of pyrogen be difficult for by evaporator section fully absorb and produce overheated, on the other hand, also because the area of dissipation of condensation segment is too small, makes the maximum of heat pipe move heat equally and be restricted, if can't make evaporator section and thermal source and condensation segment and heat abstractor keep the driving fit thermo-contact, then situation is with even more serious, cause hindering the backflow of condensed fluid, and then mummification takes place ahead of time and intensification rapidly, limit its maximal heat transfer amount by capillary force; And because the too high length/diameter ratio of heat pipe, cause causing in the process by the vapor transmission heat scattering and disappearing of heat, and make steam that part flows through heat pipe central authorities be condensed into drop in advance and be mixed in the vapor stream, even so that reduce by the speed that the steam of evaporator section heat absorption vaporization is transferred to condensation segment along steam flow channel and to block and the heat transmission of restriction steam, make the thermal resistance increase of heat pipe and cause the temperature difference between evaporator section and the condensation segment to strengthen, and the maximal heat transfer amount of reduction heat pipe, it is particularly unfavorable to transmit for the heat that uses heat pipe to grow distance.
Existing hot pipe technique is that the thickness that strengthens whole heat tube capillary structure layer increases water content wherein for the method that promotes the maximal heat transfer amount, but relatively, makes heat pipe slack-off and temperature difference increasing to the response time of temperature also; Otherwise, for the method for dwindling temperature difference is that the thickness of whole heat tube capillary structure layer of thinning reduces water content wherein, but relatively, the maximal heat transfer amount of heat pipe is reduced, as seen existing hot pipe technique can't be taken into account and promote the maximal heat transfer amount and dwindle temperature difference, has so formed more formidable contradiction.
[summary of the invention]
In view of this, being necessary to provide a kind of promotes the maximal heat transfer amount and dwindles the heat pipe of temperature difference.
A kind of heat pipe, the defeated hot cavity that comprises a sealing, its inwall is provided with capillary structure, and inclosure has an amount of working fluid in the defeated hot cavity, should defeated hot cavity be divided into evaporator section, condensation segment and be positioned between the two adiabatic section along the cavity length direction, this heat pipe also comprises the heat accumulation cavity of two sealings, and it is arranged at respectively on the corresponding evaporator section and condensation segment outer wall of this defeated hot cavity.
Compared with prior art, above-mentioned heat pipe is by being provided with a sealing heat accumulation cavity respectively on the evaporator section of heat pipe and condensation segment, bigger heat absorption and area of dissipation to be provided and to fail set capillary structure of the inside and outside tube wall of hot cavity and hydraulic fluid absorption that undergoes phase transition and the significantly increase that disengages evaporation latent heat by the heat accumulation cavity, strengthen the heat transmittability, reach maximal heat transfer amount that promotes heat pipe and the effect of dwindling temperature difference.
With reference to the accompanying drawings, the invention will be further described in conjunction with the embodiments.
[description of drawings]
Fig. 1 is the heat pipe longitdinal cross-section diagram of the present invention's first preferred embodiment.
Fig. 2 to Fig. 6 is respectively the view in transverse section of defeated hot cavity and each embodiment that the heat accumulation cavity makes up of the different profiles of heat pipe of the present invention.
Fig. 7 is the heat pipe longitdinal cross-section diagram of the present invention's second preferred embodiment.
Fig. 8 is the heat pipe longitdinal cross-section diagram of the present invention's the 3rd preferred embodiment.
Fig. 9 is the heat pipe longitdinal cross-section diagram of the present invention's the 4th preferred embodiment.
[specific embodiment]
Seeing also Fig. 1, is the longitdinal cross-section diagram for first embodiment of heat pipe of the present invention; Shown in heat pipe comprise the defeated hot cavity 10 of a sealing, its inwall is provided with the capillary structure 12 that the cooling lime set refluxes, space in capillary structure 12 inboard central authorities then is a steam channel 14, and defeated hot cavity 10 inner inclosures have an amount of hydraulic fluid and can appropriateness be evacuated to certain vacuum; This defeated hot cavity 10 can be divided into condensation segment A, evaporator section C and the adiabatic section B between the two along the function of use of cavity length direction each section according to it; Seal a sheathed heat accumulation cavity 20 respectively on the corresponding condensation segment A of this defeated hot cavity 10 and the outer wall of evaporator section C.Wherein, this defeated hot cavity 10 and heat accumulation cavity 20 are respectively by heat conductivility metal body and the metal shell made of aluminium, copper or its alloy preferably.
This heat accumulation cavity 20 comprises that a diameter is connected the annular sidewall 221 (inward flange of this sidewall 221 is also referred to as interior ring) that is provided with defeated hot cavity 10 outer walls respectively greater than cylindrical outer wall 211 (perhaps wall tool one determining deviation of defeated relatively hot cavity 10) and these cylindrical outer wall 211 two ends edge of defeated hot cavity 10 diameters; This outer wall 211 (being also referred to as outer shroud), sidewall 221 (also can be called outer wall with the outer wall combination, be shaped as the outer wall of " ㄇ " shape as the longitudinal cross-section) and fail the heat accumulation chamber that hot cavity 10 outer walls are combined to form a sealing accordingly, the inwall in this heat accumulation chamber, promptly the inner surface of this outer wall 211 and sidewall 221 and corresponding defeated hot cavity 10 condensation segment A outside wall surface also are provided with the capillary structure 22 that the cooling lime set refluxes, empty heat accumulation chamber in capillary structure 22 inboard central authorities then is a steam channel 24, and heat accumulation cavity 20 inner inclosures have an amount of hydraulic fluid and can appropriateness be evacuated to certain vacuum.
The heat accumulation cavity 20 of evaporator section C makes its evaporation and absorbs latent heat of phase change when will absorb the hydraulic fluid that the heat of external heat source passes in it, and heat is transferred to another hydraulic fluid in the defeated hot cavity 10 fast via evaporator section C tube wall, make its evaporation and absorb corresponding evaporation latent heat, the steam of this absorption latent heat transfers to condensation segment A via steam channel 14, by condensation segment A tube wall heat is transferred to hydraulic fluid in the heat accumulation cavity 20 on the condensation segment A, make its evaporation and absorb the evaporation latent heat of phase transformation and this latent heat is discharged by its wall, and the steam of defeated hot cavity 10 condensation segment A is condensed into liquid, is back to evaporator section C by capillary force again.This two heat accumulations cavity 20 has bigger heat absorption/area of dissipation, thereby makes heat pipe absorption/distribute heat in large quantities fast; In addition, the hydraulic fluid of defeated hot cavity 10 and heat accumulation cavity 20 in conjunction with and increase the whole latent heat amount that can absorb/distribute of heat pipe, can promote heat pipe maximal heat transfer ability and reduction heat pipe thermal resistance, also can dwindle the temperature difference between evaporator section C and the condensation segment A.
In the foregoing description, the inward flange that this heat accumulation cavity 20 presses close to fail hot cavity 10 is not established wall, and is combined to form the seal chamber of closed hoop with the wall of defeated hot cavity 10, seals it is sheathed on the defeated hot cavity 10 when making after or work such as welding.
Be appreciated that ground, the heat accumulation cavity of present embodiment can also be separate closing annular seal cavity, promptly, except the outer wall 211 and sidewall 221 of the foregoing description, also be provided with diameter less than outer wall 211 and connect the tubular inwall of these two sidewalls, 221 interior ring edges, this independently the heat accumulation cavity can directly be sheathed on and make this inwall be connected (as being undertaken fixedly connected) with defeated hot cavity 10 wall thermal conductances on the defeated hot cavity 10 to get final product by interference fit, soldering or heat-conducting glue etc.It is also understood that ground, the heat accumulation cavity 20 in the above embodiment of the present invention can be surrounded on the whole peripheral wall surfaces of condensation segment A of defeated hot cavity 10 and form closed annular solid; Also can be surrounded on the condensation segment A part peripheral wall surfaces of defeated hot cavity 10 and form semi-circular cavity, be " C " word shape as cross section.Be appreciated that ground again, (cross section on heat pipe is axial) shape also can be arcwall face (this moment, the heat accumulation chamber outer wall and the sidewall combination of the foregoing description were curved, as semicircle) to the heat accumulation chamber outer wall face in the foregoing description in the heat pipe longitudinal cross-section.
Capillary structure in above-mentioned defeated hot cavity 10 and the heat accumulation cavity 20 can be the combination of sintered powder formula, plough groove type, screen type, cellular etc. and above-mentioned different unimodality capillary structures.
Hydraulic fluid in above-mentioned defeated hot cavity 10 and the heat accumulation cavity 20 can be water, alcohol, liquid ammonia etc., or the combination of the single hydraulic fluid of above-mentioned difference.
Fig. 2 to Fig. 6 is the view in transverse section that is respectively each embodiment of the defeated hot cavity of different profiles of heat pipe of the present invention and the combination of heat accumulation cavity: wherein Figure 2 shows that the combination of the defeated hot cavity 10 of circle with the circular heat accumulation cavity 20 of the foregoing description, promptly ring is for circular in the sidewall 221 of this heat accumulation cavity 20, and outer wall 211 cross sections also are circular; Figure 3 shows that the combination of circular defeated hot cavity 101 and rectangle heat accumulation cavity 201, promptly ring is for circular in the sidewall of this heat accumulation cavity 201, and outer wall 212 cross sections are rectangle; Figure 4 shows that the combination of defeated hot cavity 102 of rectangle and circular heat accumulation cavity 202, promptly ring is rectangle in the sidewall of this heat accumulation cavity 202, and outer wall 213 cross sections are circular; Fig. 5 is the combination of the defeated hot cavity 103 of rectangle with rectangle heat accumulation cavity 203, and promptly ring is rectangle in the sidewall of this heat accumulation cavity 203, and outer wall 214 cross sections also are rectangle; Fig. 6 is the combination of the defeated hot cavity 104 of triangle with circular heat accumulation cavity 204, and promptly ring is triangle in the sidewall of this heat accumulation cavity 204, and outer wall 215 cross sections are circular.By the schematic diagram in above-mentioned cross section as can be known, the external form of the defeated hot cavity of heat pipe of the present invention can be different shape, and the interior contour shape of heat accumulation cavity and defeated hot cavity external form coupling, its outer contour shape can be different shape; The inwall of the inwall of defeated hot cavity and heat accumulation cavity and corresponding defeated hot chamber outer wall are equipped with capillary structure in heat pipe structure of the present invention.
Seeing also Fig. 7, is the longitdinal cross-section diagram for second embodiment of heat pipe of the present invention.The difference of itself and above-mentioned embodiment shown in Figure 1 is that present embodiment is provided with some radiating fins 26 by stretching out on the heat accumulation cavity 20 ' outside wall surface that is sheathed on defeated hot cavity 10 ' condensation segment A outer wall, increases area of dissipation to advance one one.
Seeing also Fig. 8, is the schematic diagram for the 3rd embodiment of heat pipe of the present invention; The difference of itself and first embodiment is: present embodiment is by at the seal casinghousing that vacuumize 30 of a B outer wall sheathed diameter in adiabatic section greater than defeated hot cavity 10 diameters, reach the vacuum insulation effect, when effectively overcoming the long distance of heat pipe and conducting heat because too high length/diameter ratio, cause scattering and disappearing of heat in the vapor transmission process, and make steam that part flows through heat pipe central authorities be condensed into drop in advance and be mixed in the vapor stream, thereby block or limit the transmission of steam, thereby the temperature difference of heat pipe is strengthened, and thermal resistance increases and reduces the maximal heat transfer amount of heat pipe; Therefore, present embodiment has further lifting heat pipe maximal heat transfer amount and dwindles the effect of temperature difference.
Seeing also Fig. 9, is the schematic diagram for the 4th embodiment of heat pipe of the present invention; The difference of itself and second embodiment is: present embodiment reaches the vacuum insulation effect by at the seal casinghousing 30 ' that vacuumizes of a B outer wall sheathed diameter in adiabatic section greater than defeated hot cavity 10 ' diameter.
From as can be known above-mentioned, heat pipe of the present invention with above-mentioned feature, by sheathed one accumulator tank that is sealed in outside the tube wall on the condensation segment of heat pipe and evaporator section, heat absorption and area of dissipation much larger than conventional heat pipe are provided, reach heat flux load and effective thermal contact resistance that reduces evaporator section and condensation segment of effective reduction adopting heat pipes for heat transfer; And by accumulator tank at the set capillary structure of the inside and outside tube wall of condensation segment and evaporator section, its interior hydraulic fluid is absorbed and the high-efficiency thermal biography circulation that discharges evaporation latent heat via the phase change of vaporization with condensation, reach the distribution thermal resistance that significantly promotes heat pipe maximal heat transfer amount and effectively reduce heat pipe evaporator section and condensation segment; And the sealed cavity by vacuumizing in adiabatic section outer setting one, the insulated heat of heat pipe length apart from the heat transfer high-quality is provided; Therefore, heat pipe of the present invention can significantly promote simultaneously the maximal heat transfer amount of heat pipe and significantly dwindle temperature difference between evaporator section and the condensation segment.
Claims (11)
1. heat pipe, the defeated hot cavity that comprises a sealing, its inwall is provided with capillary structure, and inclosure has an amount of working fluid in the defeated hot cavity, should defeated hot cavity be divided into evaporator section, condensation segment and be positioned between the two adiabatic section along the cavity length direction, it is characterized in that: this heat pipe also comprises the heat accumulation cavity of two sealings, and it is arranged at respectively on the corresponding evaporator section and condensation segment outer wall of this defeated hot cavity.
2. heat pipe as claimed in claim 1 is characterized in that: above-mentioned two heat accumulation cavitys are on the corresponding evaporator section and condensation segment outer wall that are sheathed on this defeated hot cavity respectively.
3. heat pipe as claimed in claim 1 is characterized in that: above-mentioned heat accumulation cavity is annular seal cavity independently, and it comprises and the outer wall of defeated hot cavity wall mask one determining deviation and the inwall of fitting with defeated hot cavity wall.
4. heat pipe as claimed in claim 3 is characterized in that: above-mentioned heat accumulation cavity inner wall face is equipped with capillary structure, and wherein inclosure has an amount of hydraulic fluid.
5. heat pipe as claimed in claim 1 is characterized in that: above-mentioned heat accumulation cavity comprises that an outer wall and defeated hot cavity wall are combined to form the annular seal chamber, and this inner cavity surface is equipped with capillary structure, and wherein inclosure has an amount of hydraulic fluid.
6. as claim 3 or 5 described heat pipes, it is characterized in that: above-mentioned heat accumulation chamber outer wall is shaped as " ㄇ " shape or semicircle in the longitudinal cross-section.
7. as claim 3 or 5 described heat pipes, it is characterized in that: above-mentioned heat accumulation cavity is surrounded on the whole peripheral wall surfaces of defeated hot cavity and forms closed annular solid.
8. as claim 3 or 5 described heat pipes, it is characterized in that: above-mentioned heat accumulation cavity is surrounded on the part peripheral wall surfaces of defeated hot cavity and forms the semi-ring body.
9. heat pipe as claimed in claim 1 is characterized in that: the heat accumulation chamber outer wall facing epitaxy of above-mentioned corresponding condensation segment is stretched and is provided with some radiating fins.
10. heat pipe as claimed in claim 1 is characterized in that: the corresponding adiabatic section of above-mentioned defeated hot cavity outside wall surface forms the annular compartment of vacuum around being provided with seal casinghousing.
11. as each described heat pipe in the claim 1 to 5, it is characterized in that: the wall shape of cross section of above-mentioned defeated hot cavity is one of circular, ellipse, polygon or its complex, ring is corresponding with the wall shape of cross section of defeated hot cavity in the cross section of this heat accumulation cavity, and its external wall cross-section is one of circle, ellipse, polygon or its complex.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100603042A CN100529639C (en) | 2006-04-14 | 2006-04-14 | Heat pipe |
| US11/309,381 US20070240852A1 (en) | 2006-04-14 | 2006-08-02 | Heat pipe with heat reservoirs at both evaporating and condensing sections thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100603042A CN100529639C (en) | 2006-04-14 | 2006-04-14 | Heat pipe |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101055155A true CN101055155A (en) | 2007-10-17 |
| CN100529639C CN100529639C (en) | 2009-08-19 |
Family
ID=38603728
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006100603042A Expired - Fee Related CN100529639C (en) | 2006-04-14 | 2006-04-14 | Heat pipe |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US20070240852A1 (en) |
| CN (1) | CN100529639C (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102644124A (en) * | 2012-03-30 | 2012-08-22 | 宏大研究院有限公司 | Spinning manifold for non-woven fabric equipment |
| CN108155761A (en) * | 2018-01-31 | 2018-06-12 | 华南理工大学 | A kind of motor of automobile motor stator module application for strengthening heat management |
| CN108281736A (en) * | 2018-01-31 | 2018-07-13 | 陈攀攀 | A kind of cooling device that rectangle power battery is stacked |
| CN109588015A (en) * | 2018-12-21 | 2019-04-05 | 中国航空工业集团公司西安航空计算技术研究所 | A kind of distribution heat reservoir |
| CN112421890A (en) * | 2020-10-28 | 2021-02-26 | 中国科学院电工研究所 | Space motor cooling system |
| CN112611243A (en) * | 2020-12-23 | 2021-04-06 | 长春工程学院 | Novel strengthen air heat transfer phase transition heat accumulation device |
| CN114440678A (en) * | 2022-02-17 | 2022-05-06 | 郭鹏杰 | Multidimensional heat pipe and electronic equipment |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100529640C (en) * | 2006-04-14 | 2009-08-19 | 富准精密工业(深圳)有限公司 | Heat pipe |
| US20080264608A1 (en) * | 2007-04-30 | 2008-10-30 | Trentent Tye | Cooling mechanism comprising a heat pipe and water block |
| FR2919922B1 (en) * | 2007-08-08 | 2009-10-30 | Astrium Sas Soc Par Actions Si | PASSIVE THERMAL CONTROL DEVICE WITH MICRO BUCKLE FLUID WITH CAPILLARY PUMPING |
| CN101907412B (en) * | 2009-06-03 | 2013-03-06 | 富瑞精密组件（昆山）有限公司 | Heat pipe |
| US20110067416A1 (en) * | 2009-09-24 | 2011-03-24 | Shao-Hsiung Chang | Thermal exchanging device |
| US9599408B1 (en) * | 2012-03-03 | 2017-03-21 | Advanced Cooling Technologies, Inc. | Loop heat pipe evaporator including a second heat pipe |
| US9772143B2 (en) * | 2013-04-25 | 2017-09-26 | Asia Vital Components Co., Ltd. | Thermal module |
| US10352625B2 (en) * | 2013-04-25 | 2019-07-16 | Asia Vital Components Co., Ltd. | Thermal module |
| CN104634144A (en) * | 2015-02-10 | 2015-05-20 | 季弘 | Heat pipe type food cooling bar |
| US11598584B2 (en) * | 2020-04-15 | 2023-03-07 | Asia Vital Components Co., Ltd. | Dual heat transfer structure |
| US11800684B2 (en) * | 2021-01-19 | 2023-10-24 | GM Global Technology Operations LLC | Heat pipe with multiple stages of cooling |
| FR3130019A1 (en) * | 2021-12-07 | 2023-06-09 | Airbus Defence And Space Sas | One-way two-phase heat transfer structure |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US3666005A (en) * | 1970-07-06 | 1972-05-30 | Robert David Moore Jr | Segmented heat pipe |
| US4220195A (en) * | 1979-05-24 | 1980-09-02 | The United States Of America As Represented By The Secretary Of The Navy | Ion drag pumped heat pipe |
| US4463798A (en) * | 1981-01-07 | 1984-08-07 | The Boeing Company | Electrostatically pumped heat pipe and method |
| US4857421A (en) * | 1988-11-14 | 1989-08-15 | Thermacore, Inc. | Alkali metal thermoelectric genreator |
| US5219516A (en) * | 1992-06-16 | 1993-06-15 | Thermacore, Inc. | Thermionic generator module with heat pipes |
| US20040118553A1 (en) * | 2002-12-23 | 2004-06-24 | Graftech, Inc. | Flexible graphite thermal management devices |
| CN1892206A (en) * | 2005-07-08 | 2007-01-10 | 鸿富锦精密工业（深圳）有限公司 | Heat-pipe measuring device |
| CN100513973C (en) * | 2006-04-14 | 2009-07-15 | 富准精密工业(深圳)有限公司 | Heat pipe |
| CN100529640C (en) * | 2006-04-14 | 2009-08-19 | 富准精密工业(深圳)有限公司 | Heat pipe |
-
2006
- 2006-04-14 CN CNB2006100603042A patent/CN100529639C/en not_active Expired - Fee Related
- 2006-08-02 US US11/309,381 patent/US20070240852A1/en not_active Abandoned
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102644124A (en) * | 2012-03-30 | 2012-08-22 | 宏大研究院有限公司 | Spinning manifold for non-woven fabric equipment |
| CN108155761A (en) * | 2018-01-31 | 2018-06-12 | 华南理工大学 | A kind of motor of automobile motor stator module application for strengthening heat management |
| CN108281736A (en) * | 2018-01-31 | 2018-07-13 | 陈攀攀 | A kind of cooling device that rectangle power battery is stacked |
| CN109588015A (en) * | 2018-12-21 | 2019-04-05 | 中国航空工业集团公司西安航空计算技术研究所 | A kind of distribution heat reservoir |
| CN109588015B (en) * | 2018-12-21 | 2020-12-29 | 中国航空工业集团公司西安航空计算技术研究所 | Distributed heat storage system |
| CN112421890A (en) * | 2020-10-28 | 2021-02-26 | 中国科学院电工研究所 | Space motor cooling system |
| CN112421890B (en) * | 2020-10-28 | 2021-12-07 | 中国科学院电工研究所 | Space motor cooling system |
| CN112611243A (en) * | 2020-12-23 | 2021-04-06 | 长春工程学院 | Novel strengthen air heat transfer phase transition heat accumulation device |
| CN112611243B (en) * | 2020-12-23 | 2022-09-30 | 长春工程学院 | Novel strengthen air heat transfer phase transition heat accumulation device |
| CN114440678A (en) * | 2022-02-17 | 2022-05-06 | 郭鹏杰 | Multidimensional heat pipe and electronic equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100529639C (en) | 2009-08-19 |
| US20070240852A1 (en) | 2007-10-18 |
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