1279515 中央之蒸、/"L提前冷凝為液滴而混合於蒸汽流中，從而阻塞 或限制蒸汽之傳遞，如此導致該熱管之熱阻增加並進一步 降低熱管之隶大傳熱量；再者，由於現有技術中熱管具有 均勻之毛細結構層厚度及蒸汽流道管徑，以致由蒸發段吸 熱汽化之蒸汽沿蒸汽流道傳輸到冷凝段之速度降低，助長 ’熱量之散失並導致蒸發段至冷凝段之溫度差（ΔΤ)加大。現 有技術中對於提升熱管最大傳熱量（Qmax)之方法係加大整 鲁支熱管毛細結構層之厚度使其中含水量增加，但相對地， 卻也使熱管之反應時間變慢及溫度差（ΔΤ)加大；反之，對 於縮小溫度差（ΔΤ)之方法係薄化整支熱管毛細結構層之厚 度使其中之含水量降低，但相對地，卻也使熱管之最大傳 熱量（Qmax)降低。 【發明内容】 有鑒於此，有必要提供一種能降低熱阻及提升熱管最 春大傳熱量並能縮小冷凝段與蒸發段間溫度差之熱管。 一種熱管，包括一密封腔體，其内裝設有適量工作液 體’該腔體内壁形成有便於工作液體回流之毛細結構，該 毛細結構内表面圍成一沿熱管長度方向延伸之蒸汽流道， 該熱管包括一蒸發段、一冷凝段及一位於二者之間之絕熱 段，該蒸汽流道内壁形成有一端口大一端口小之喷嘴，其 中小端口朝向冷凝段。 該熱管藉由在蒸汽流道中設置喷嘴，對蒸汽流產生加 1279515 '速作用，可使蒸汽流更快速傳輸到冷凝段冷卻並釋放出熱 量，加速工作液體在管内之迴圈以縮小蒸發段至冷凝段之 溫度差（ΔΤ)，達到降低熱阻及提升熱管最大傳熱量（Qmax) 之功效。 、 下面參照附圖結合實施例對本發明作進一步說明。 【實施方式】 圖1為本發明實施例一，熱管10包括一密封腔體110， p該密封腔體110包括一呈空心圓柱狀之管壁112和分別位於 該管壁兩端之一封口 114及一底部116。緊貼該管壁112内表 面分佈有毛細結構130，該毛細結構130可以為燒結粉末 式、溝槽式、絲網式、蜂巢式以及上述不同單一型式毛細 結構之組合，由毛細結構130内表面圍成一中空並沿熱管10 長度方向延伸之蒸汽流道150，該蒸汽流道150内填充有適 量工作液體（圖未示）。 該熱管10沿其長度方向可分為一蒸發段120、一冷凝段 • 160及一位於蒸發段120和冷凝段160之間之絕熱段140，.該 •蒸發段120用以靠近外部熱源吸收熱量，並且將熱量傳遞給 '蒸汽流道150内之工作液體使其蒸發，該絕熱段140用以在 與外界隔熱狀態下傳輸蒸汽，該冷凝段160遠離外部熱源以 將蒸汽冷凝成液體，並將熱量藉由管壁Π2和底部116傳遞 到密封腔體110外。 該蒸汽流道150沿熱管10長度方向可分為直管道152、 喷嘴154、擴散管道156、直管道158四部分。該直管道152 8 1279515 位於蒸發段120—端，其周圍毛細結構130厚度均勻。在蒸 發段120與絕熱段140之邊界處，毛細結構130厚度沿蒸發段 120到絕熱段140方向逐漸增加，蒸汽流道150截面逐漸變 窄，其周圍毛細結構130内表界面形成一張角形狀之喷嘴 、154。從該喷嘴154末端向冷凝段160繼續延伸，毛細結構130 厚度逐漸減小使得蒸汽流道150内形成逐漸擴張之擴散管 .道156,在接近絕熱段140與冷凝段160邊界處，毛細結構130 厚度保持均勻以形成一繼續向冷凝段160延伸之直管道 ® 158。其中，喷嘴154、擴散管道156及直管道158構成了一 蒸汽喷流管道155。另外，該喷嘴154也可設置于絕熱段140。 該熱管10之工作原理為，當蒸發段120將吸收外部熱源 之熱量傳給密封腔體110内之工作液體使其蒸發，當蒸汽到 達喷嘴154處時，該喷嘴154為一漸縮管，根據液體連續性 原理，即同一流管中任一橫截面處之截面面積和該處液體 流速之乘積為一恒量，以及液體連續性流動方程2=5x7 (其 鲁中，Q代表單位時間内流過管道某一截面之液體體積；S代 .表流管之截面面積；V代表液體在該截面處之流速）可知， 流管之截面面積大處流速小，截面面積小處流速大。因此， 蒸汽在喷嘴154直徑較小處之速度加大，並逐漸加速向冷凝 段160方向流動，同時，由於在朝冷凝段160之擴散管道156 逐漸增加亦有利於降低蒸汽回流到冷凝段160之流阻，因此 藉由該蒸汽喷流管道155之加速及穩流作用，可使蒸汽更快 速傳輸到冷凝段160冷卻並釋放出熱量，且防止蒸汽傳輸過 程中因熱量之散失而提早發生冷凝現象所造成對傳輸中之 9 1279515 蒸汽流阻加大之負面效應，該蒸汽喷流管道155可在其外形 接近流線時達到99%以上之高效率泄流係數（dlSCharge coefficient)，因此具有 氏流阻、無需外加動力即可產生知、疋 之加速擴散喷流特徵。另外，當工作液體在冷凝段160冷卻 成液體後，其將在毛細結構130毛細力作用下朝蒸發段120 方向回流，由於絕熱段140之毛細結構層厚度逐漸增加’冷 ‘凝液體回流到蒸發段120之流阻逐漸滅小，有利於工作液體 •迅速回流到蒸發段120。因此，該熱管10可有效降低熱阻並 能有效提升熱管10之最大傳熱量（Qinax) ° 圖2為本發明實施例二之一熱管20，其與實施例一之熱 管10所不同之處在於，蒸汽喷流管道255取代了實施例一中 之蒸汽喷流管道155，該蒸汽喷流管道255中噴嘴254、擴散 管道256及部分直管道258之毛細結構内壁上密貼設置了一 蒸汽噴流管257，該蒸汽喷流管257由成形金屬箔片或成形 薄管製成，其設置於蒸汽喷流管道255之内壁上以形成二^ _液隔離層，可有效降低蒸汽流與毛細結構230界面回流液體 、之相互干擾。與熱管10相比較，該熱管20由於增加了蒸汽 ‘噴流管257可進一步降低熱阻，提高蒸汽流和回流液體在官 中運動速度，縮小蒸發段220至冷凝段260間之溫度差（ΔΤ) ° 對於熱管20，藉由調整該喷嘴254之張角和直管道252 長度，可以控制蒸發段220之毛細結構230厚度；同樣地’ 藉由調整該擴散管道256之張角和直管道258之長度’ <以 控制冷凝段260之毛細結構230厚度。藉由在蒸汽喷流管道 255之前後搭配具有各種不同厚度毛細結構230之蒸發段 1279515 ' 220及冷凝段260，或在蒸發段220及冷凝段260中採用不同 形式之毛細結構形式，例如燒結粉末式、溝槽式、絲網式、 蜂巢式以及上述不同單一型式毛細結構之組合等。 圖3為本發明實施例三之一熱管30，其與實施例二熱管 20之區別在於，本實施例藉由改變熱管30之蒸發段320及冷 凝段360毛細結構330厚度之方式以取代實施例二中蒸發段 220及冷凝段260具有相同毛細結構層之厚度，其中，蒸發 段320較冷凝段360之毛細結構330薄，而其對應之蒸汽流道 > 350較冷凝段360之蒸汽流道350寬。 圖4為本發明實施例四之一熱管40，其與實施例二熱管 20之區別在於，本實施例藉由改變熱管40之蒸發段420及冷 凝段460毛細結構430厚度之方式以取代實施例二中蒸發段 220及冷凝段260具有相同毛細結構層之厚度，其中，蒸發 段420較冷凝段460之毛細結構430厚，而其對應之蒸汽流道 450較冷凝段460之蒸汽流道450窄。 | 本發明實施例熱管10、20、30、40藉由在毛細結構130、 -230、330、430内壁上設置蒸汽喷流管道155、255、355、 455，可降低蒸汽流動時與毛細結構界面回流液體之交互干 擾，加速工作液體在管内之循環以縮小蒸發段至冷凝段之 溫度差（ΔΤ);而且，藉由單獨控制蒸發段及冷凝段毛細結 構層厚度可以分別滿足蒸發段及冷凝段在不同應用場合下 之熱傳輸機制。從以上所述内容中不難看出，只要保證喷 嘴小端口朝向冷凝段，該喷嘴也可設置于蒸發段或者冷凝 段，同樣可以達到加速蒸汽在蒸汽流道中流動目的。 π 1279515 1 綜上所述，本發明之熱管可有效降低熱阻及提升熱管 最大傳熱量並能縮小冷凝段與蒸發段間溫度差。 綜上所述，本發明符合發明專利要件，爰依法提出專 利申請。惟，以上該者僅為本發明之較佳實施例，舉凡熟 悉本案技藝之人士，在爰依本發明精神所作之等效修飾或 變化，皆應涵蓋於以下之申請專利範圍内。 【圖式簡單說明】 圖1係本發明熱管之實施例一縱向剖面示意圖。1279515 The central steaming, /"L is condensed into droplets in advance and mixed in the steam stream, thereby blocking or limiting the transfer of steam, thus causing the heat resistance of the heat pipe to increase and further reducing the heat transfer capacity of the heat pipe; Since the heat pipe of the prior art has a uniform capillary layer thickness and a steam channel diameter, the velocity of the vapor vaporized by the vaporization section of the evaporation section to the condensation section along the steam channel is reduced, which promotes the loss of heat and causes the evaporation section to condense. The temperature difference (ΔΤ) of the segment is increased. In the prior art, the method for increasing the maximum heat transfer amount (Qmax) of the heat pipe is to increase the thickness of the capillary structure layer of the heat pipe to increase the water content therein, but relatively, the reaction time of the heat pipe is slowed down and the temperature difference (ΔΤ) The method of narrowing the temperature difference (ΔΤ) is to thin the thickness of the capillary structure layer of the entire heat pipe to reduce the water content therein, but relatively, the maximum heat transfer amount (Qmax) of the heat pipe is also lowered. SUMMARY OF THE INVENTION In view of the above, it is necessary to provide a heat pipe capable of reducing thermal resistance and increasing the maximum heat transfer amount of the heat pipe and reducing the temperature difference between the condensation section and the evaporation section. A heat pipe includes a sealed cavity having an appropriate amount of working liquid therein. The inner wall of the cavity is formed with a capillary structure for facilitating the return of the working liquid. The inner surface of the capillary structure encloses a steam flow path extending along the length of the heat pipe. The heat pipe comprises an evaporation section, a condensation section and an adiabatic section therebetween. The inner wall of the steam flow channel is formed with a nozzle having a large port and a small port, wherein the small port faces the condensation section. By providing a nozzle in the steam flow channel, the heat pipe adds a 1279515 'speed effect to the steam flow, so that the steam flow can be more quickly transmitted to the condensation section to cool and release heat, and accelerate the circulation of the working liquid in the tube to reduce the evaporation section to The temperature difference (ΔΤ) of the condensation section achieves the effect of reducing the thermal resistance and increasing the maximum heat transfer (Qmax) of the heat pipe. The present invention will be further described below in conjunction with the embodiments with reference to the accompanying drawings. [Embodiment] FIG. 1 is a first embodiment of the present invention. The heat pipe 10 includes a sealed cavity 110. The sealed cavity 110 includes a hollow cylindrical tubular wall 112 and a port 114 at each end of the tubular wall. And a bottom 116. A capillary structure 130 is disposed on the inner surface of the tube wall 112. The capillary structure 130 may be a sintered powder type, a groove type, a wire mesh type, a honeycomb type, and a combination of the above different single type capillary structures, and the inner surface of the capillary structure 130 A steam flow passage 150 is formed which is hollow and extends along the length of the heat pipe 10, and the steam flow passage 150 is filled with an appropriate amount of working liquid (not shown). The heat pipe 10 can be divided along its length into an evaporation section 120, a condensation section 160 and an adiabatic section 140 between the evaporation section 120 and the condensation section 160. The evaporation section 120 is used to absorb heat from an external heat source. And transferring heat to the working liquid in the 'steam flow passage 150 for evaporating, the heat insulating section 140 is for transmitting steam in a state of being insulated from the outside, the condensation section 160 being away from the external heat source to condense the steam into a liquid, and Heat is transferred to the outside of the sealed cavity 110 by the tube wall 2 and the bottom 116. The steam flow path 150 can be divided into four parts: a straight pipe 152, a nozzle 154, a diffusion pipe 156, and a straight pipe 158 along the longitudinal direction of the heat pipe 10. The straight pipe 152 8 1279515 is located at the end of the evaporation section 120, and the capillary structure 130 around it is uniform in thickness. At the boundary between the evaporation section 120 and the adiabatic section 140, the thickness of the capillary structure 130 gradually increases along the evaporation section 120 to the adiabatic section 140, the cross section of the steam flow passage 150 is gradually narrowed, and the surface interface of the surrounding capillary structure 130 forms an angular shape. Nozzle, 154. From the end of the nozzle 154 to the condensing section 160, the capillary structure 130 is gradually reduced in thickness such that a gradually expanding diffuser tube 156 is formed in the vapor flow path 150. At the boundary between the insulating section 140 and the condensing section 160, the capillary structure 130 The thickness remains uniform to form a straight tube® 158 that continues to extend toward the condensing section 160. Among them, the nozzle 154, the diffusion duct 156 and the straight duct 158 constitute a steam jet pipe 155. Additionally, the nozzle 154 can also be disposed in the adiabatic section 140. The working principle of the heat pipe 10 is that when the evaporation section 120 transfers the heat of the external heat source to the working liquid in the sealing cavity 110 to evaporate, when the steam reaches the nozzle 154, the nozzle 154 is a tapered tube, according to The principle of liquid continuity, that is, the product of the cross-sectional area at any cross section in the same flow tube and the liquid flow rate at that point is a constant, and the liquid continuity flow equation 2 = 5x7 (in which Lu represents the flow per unit time) The liquid volume of a certain section of the pipeline; the cross-sectional area of the S-flow tube; V represents the flow rate of the liquid at the cross-section. It can be seen that the flow velocity of the flow tube is small, the flow velocity is small, and the flow velocity is small at a small cross-sectional area. Therefore, the velocity of the steam at the smaller diameter of the nozzle 154 is increased and gradually accelerates toward the condensing section 160, and at the same time, the gradual increase of the diffusion duct 156 toward the condensing section 160 is also advantageous for reducing the reflux of the steam to the condensing section 160. Flow resistance, so that by the acceleration and steady flow of the steam jet pipe 155, steam can be more quickly transferred to the condensing section 160 to cool and release heat, and prevent condensation from occurring due to heat loss during steam transfer. The negative effect of the increased flow resistance of the 9 1279515 in the transmission, the steam jet pipe 155 can achieve a high efficiency discharge coefficient (dlSCharge coefficient) of more than 99% when its shape is close to the flow line, thus having a flow Resistance, no need for external power to generate the characteristics of accelerated diffusion jets. In addition, when the working liquid is cooled to a liquid in the condensation section 160, it will flow back toward the evaporation section 120 under the capillary force of the capillary structure 130, and the thickness of the capillary structure layer of the adiabatic section 140 gradually increases, and the 'cold' condensation liquid flows back to the evaporation. The flow resistance of the segment 120 is gradually reduced, which is beneficial to the working fluid and the rapid return to the evaporation section 120. Therefore, the heat pipe 10 can effectively reduce the thermal resistance and can effectively increase the maximum heat transfer amount of the heat pipe 10 (Qinax). FIG. 2 is a heat pipe 20 according to the second embodiment of the present invention, which is different from the heat pipe 10 of the first embodiment. The steam jet pipe 255 replaces the steam jet pipe 155 in the first embodiment. The steam jet pipe 255 has a steam jet pipe disposed on the inner wall of the capillary structure 254, the diffusing pipe 256 and the partial straight pipe 258. 257, the steam jet pipe 257 is made of a formed metal foil or a formed thin tube, and is disposed on the inner wall of the steam jet pipe 255 to form a liquid separation layer, which can effectively reduce the interface between the steam flow and the capillary structure 230. The liquids are refluxed and interfere with each other. Compared with the heat pipe 10, the heat pipe 20 can further reduce the thermal resistance due to the addition of the steam 'jet pipe 257, increase the velocity of the steam flow and the return liquid in the official, and reduce the temperature difference (ΔΤ) between the evaporation section 220 and the condensation section 260. ° For the heat pipe 20, by adjusting the opening angle of the nozzle 254 and the length of the straight pipe 252, the thickness of the capillary structure 230 of the evaporation section 220 can be controlled; likewise 'by adjusting the opening angle of the diffusion pipe 256 and the length of the straight pipe 258' To control the thickness of the capillary structure 230 of the condensation section 260. By using the evaporation section 1279515' 220 and the condensation section 260 having various thicknesses of the capillary structure 230 before or after the steam jet pipe 255, or in the evaporation section 220 and the condensation section 260, different forms of capillary structure, such as sintered powder, are used. Type, groove type, wire mesh type, honeycomb type, and combinations of different single type capillary structures described above. 3 is a heat pipe 30 according to a third embodiment of the present invention, which is different from the heat pipe 20 of the second embodiment in that the embodiment is replaced by changing the thickness of the evaporation section 320 of the heat pipe 30 and the capillary structure 330 of the condensation section 360. The second intermediate evaporation section 220 and the condensation section 260 have the same thickness of the capillary structure layer, wherein the evaporation section 320 is thinner than the capillary structure 330 of the condensation section 360, and the corresponding steam flow channel > 350 is more vaporous than the condensation section 360. 350 wide. 4 is a heat pipe 40 according to a fourth embodiment of the present invention, which is different from the heat pipe 20 of the second embodiment in that the embodiment is replaced by changing the thickness of the evaporation section 420 and the condensation section 460 of the heat pipe 40. The second intermediate evaporation section 220 and the condensation section 260 have the same thickness of the capillary structure layer, wherein the evaporation section 420 is thicker than the capillary structure 430 of the condensation section 460, and the corresponding steam flow path 450 is narrower than the steam flow path 450 of the condensation section 460. . In the embodiment of the present invention, the heat pipes 10, 20, 30, 40 can reduce the flow of steam and the capillary structure by providing steam jet pipes 155, 255, 355, and 455 on the inner walls of the capillary structures 130, -230, 330, and 430. The mutual interference of the reflux liquid accelerates the circulation of the working liquid in the tube to reduce the temperature difference (ΔΤ) between the evaporation section and the condensation section; and, by separately controlling the thickness of the evaporation section and the condensing section capillary structure layer, the evaporation section and the condensation section can be respectively satisfied. Heat transfer mechanism in different applications. It is not difficult to see from the above that as long as the nozzle port is made to face the condensation section, the nozzle can also be placed in the evaporation section or the condensation section, and the purpose of accelerating the flow of steam in the steam passage can also be achieved. π 1279515 1 In summary, the heat pipe of the present invention can effectively reduce the thermal resistance and increase the maximum heat transfer amount of the heat pipe and can reduce the temperature difference between the condensation section and the evaporation section. In summary, the present invention complies with the requirements of the invention patent and submits a patent application according to law. The above is only the preferred embodiment of the present invention, and equivalent modifications or variations made by those skilled in the art will be included in the following claims. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal cross-sectional view showing an embodiment of a heat pipe of the present invention.
I 圖2係本發明熱管之實施例二縱向剖面示意圖。 圖3係本發明熱管之實施例三縱向剖面示意圖。 圖4係本發明熱管之實施例四縱向剖面示意圖。 【主要元件符號說明】 熱管 10,20,30,40 密封腔體 110 管壁 112 封口 114 底部 116 蒸發段 120,220,320,420 毛細結構 130,230,330,430 絕熱段 140 蒸氣流道 150,350,450 直管道 152,252 喷嘴 154,254 蒸氣喷流管道 155,255,355,455 擴散管道 156,256 直管道 158,258 冷凝段 160,260,360,460 蒸氣喷流管 257 12I Fig. 2 is a longitudinal cross-sectional view showing the second embodiment of the heat pipe of the present invention. Figure 3 is a longitudinal cross-sectional view showing the third embodiment of the heat pipe of the present invention. Figure 4 is a schematic longitudinal cross-sectional view showing the fourth embodiment of the heat pipe of the present invention. [Main component symbol description] Heat pipe 10, 20, 30, 40 Sealing cavity 110 Pipe wall 112 Sealing 114 Bottom 116 Evaporation section 120, 220, 320, 420 Capillary structure 130, 230, 330, 430 Adiabatic section 140 Vapor flow path 150, 350, 450 Straight pipe 152, 252 Nozzle 154, 254 Vapor jet pipe 155, 255, 355, 455 Diffusion pipe 156,256 straight pipe 158,258 condensation section 160,260,360,460 steam jet pipe 257 12