1292470 ‘ 蒸發段乾化，熱管急速升溫，限制其最大傳熱能力。 另外，由於熱管過高之長度/直徑比，導致蒸汽傳輸過 \ 程中熱量之散失，使部分流過熱管中央之蒸汽提前冷 ' 凝爲液體，從而阻塞或限制蒸汽之流動，使熱管之熱 阻增加並降低熱管之最大傳熱量。 【發明内容】 有鑒於此，有必要提供一種熱傳效率高之熱管。 一種熱管，包括一密封殼體，殼體内腔内裝入適 量工作流體，該殼體内壁設有毛細結構，該熱管包括 冷凝段、蒸發段及位於二者之間之絕熱段，該密封殼 體内設有朝向冷凝段之喷嘴，該喷嘴為設置於蒸汽通 道中之漸縮管。 與習知技術相比，由於在熱管密封殼體内設有朝 向冷凝段之喷嘴，當蒸發段將吸收外界熱源之熱量傳 給密封殼體内之工作流體使其蒸發，並通過該喷嘴之 加速作用，可使蒸汽流更快速傳輸到冷凝段冷卻並釋 出熱量，且可降低蒸汽流與毛細結構介面之交互干 擾，達到降低熱阻及提升熱管最大傳熱能力之功效。 【實施方式】 以下參照圖1至圖3，就本發明熱管之較佳實施 例詳加說明，俾利完全瞭解。本發明僅以圓管爲例對 主要技術特徵進行說明。 圖1係本發明熱管之第一實施例之剖面示意圖。 1292470 該熱管爲直型熱管，包括一密封殼體100、一層毛細 結構200、以及一喷嘴300。該密封殼體1〇〇兩端分 別係一封口 140及一底部120構成，該密封殼體1〇〇 内裝入適I工作流體（圖未示），該工作流體可遇熱 蒸發爲蒸汽，遇冷冷凝爲液體。該毛細結構200設置 於該密封殼體100内壁供冷凝液體回流，而在毛細結 構200中央之空間則爲蒸汽通道。該毛細結構200可 以爲燒結粉末、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。該熱管依次區分有蒸發 段400、絕熱段500、冷凝段600三個部分。其中， 蒸發段400和冷凝段600分別位於兩端，絕熱段500 位於蒸發段400和冷凝段600之間。喷嘴300設置於 蒸汽通道中接近蒸發段400與絕熱段500之邊界並朝 向冷凝段600，但該喷嘴300之位置不限於此，亦可 設置于絕熱段500上。喷嘴300朝向冷凝段600之一 端直徑較小，相應地，喷嘴300在此處截面面積最小， 喷嘴300爲一漸縮管。根據流體連續性原理——同一 流管中任一橫截面處之截面面積和該處流體流速之 乘積爲一恒量，以及流體連續性流動方程2 = (其 中’ Q代表單位時間内流過流管某一截面之流體體 積；S代表流管之截面面積；v代表流體在該截面處 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300直徑較小處之 12924701292470 ‘ The evaporation section is dried and the heat pipe is rapidly warming up to limit its maximum heat transfer capacity. In addition, due to the excessive length/diameter ratio of the heat pipe, the heat transfer in the steam transfer process causes the steam in the center of the partial heat transfer pipe to be cold-condensed into a liquid, thereby blocking or restricting the flow of the steam, so that the heat of the heat pipe The resistance increases and reduces the maximum heat transfer of the heat pipe. SUMMARY OF THE INVENTION In view of the above, it is necessary to provide a heat pipe having high heat transfer efficiency. A heat pipe includes a sealed casing, wherein a proper amount of working fluid is placed in the inner cavity of the casing, and the inner wall of the casing is provided with a capillary structure, and the heat pipe comprises a condensation section, an evaporation section and a heat insulating section between the sealing shell The body is provided with a nozzle facing the condensation section, which is a tapered tube disposed in the steam passage. Compared with the prior art, since the nozzle facing the condensation section is provided in the heat pipe sealing housing, the evaporation section transmits the heat of the external heat source to the working fluid in the sealing casing to evaporate and accelerate through the nozzle. The function can make the steam flow transfer to the condensing section for cooling and release heat, and can reduce the interaction between the steam flow and the capillary structure interface, thereby reducing the thermal resistance and improving the maximum heat transfer capacity of the heat pipe. [Embodiment] Hereinafter, a preferred embodiment of the heat pipe of the present invention will be described in detail with reference to Figs. 1 to 3, and the profit is fully understood. The main technical features of the present invention will be described by taking a circular tube as an example. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic cross-sectional view showing a first embodiment of a heat pipe of the present invention. 1292470 The heat pipe is a straight heat pipe comprising a sealed casing 100, a capillary structure 200, and a nozzle 300. The two ends of the sealing shell 1 are respectively formed with a mouth 140 and a bottom 120. The sealing shell 1 is filled with a suitable working fluid (not shown), and the working fluid can be evaporated into steam by heat. Condensate into a liquid in case of cold. The capillary structure 200 is disposed on the inner wall of the sealed casing 100 for condensed liquid to recirculate, and the space in the center of the capillary structure 200 is a steam passage. The capillary structure 200 can be a combination of sintered powder, grooved, wire mesh, honeycomb, and a plurality of capillary structures of the above. The heat pipe is divided into three parts: an evaporation section 400, an adiabatic section 500, and a condensation section 600. Wherein, the evaporation section 400 and the condensation section 600 are respectively located at both ends, and the adiabatic section 500 is located between the evaporation section 400 and the condensation section 600. The nozzle 300 is disposed in the steam passage near the boundary between the evaporation section 400 and the adiabatic section 500 and faces the condensation section 600, but the position of the nozzle 300 is not limited thereto, and may be disposed on the heat insulating section 500. The nozzle 300 has a smaller diameter toward one end of the condensation section 600. Accordingly, the nozzle 300 has a minimum cross-sectional area therein, and the nozzle 300 is a tapered tube. According to the principle of fluid continuity—the product of the cross-sectional area at any cross section in the same flow tube and the fluid velocity at that point is a constant, and the fluid continuity flow equation 2 = (where 'Q represents flow through the flow tube per unit time) The fluid volume of a certain section; S represents the cross-sectional area of the flow tube; v represents the flow velocity of the fluid at the cross-section. It can be seen that the flow velocity of the flow tube is large, and the flow velocity is small, and the flow velocity is small at a small cross-sectional area. Therefore, the steam is at a small diameter of the nozzle 300 1292470
速度加大，哈嘴如A 流動之作用。、蒸汽向冷凝段刪方向 將吸收外界熱源之熱量傳 ★ 内之工作液體使其蒸發，使蒸發段4〇〇 条/飞體積增加，同時蒸發段4〇〇 β之壓強增大， 驅動蒸汽向冷凝段_之方向流動 嘴300之輕0士 田…/飞々丨l靭判嘴The speed is increased, and the mouth of the mouth is like the flow of A. The steam is removed from the condensation section to absorb the heat from the external heat source. The working liquid inside is evaporated to increase the volume of the evaporation section 4, and the pressure of the evaporation section 4〇〇β increases, driving the steam direction. Condensation section _ direction of the flow nozzle 300 light 0 Shi Tian ... / fly 々丨 l tough mouth
#★、旱]、為日守，通過該喷嘴300之加速作用，可 使更快速傳輸到冷凝段_冷卻並釋出熱量。 ^直形熱f蒸汽流場發展狀況可明確看出高速 f汽自噴嘴_的小口噴出後將以更高的速度衝向冷 f亚同時向管壁方向擴散，其橫向擴散的快 慢與蒸汽的速度呈反比，如果蒸汽的主流速度(main stream vel〇clty)越快，顯示當蒸汽由噴嘴細的小口 射出並橫向擴散到接觸管壁之前的軸向距離也越 長，亦即蒸汽流在該距離内將大幅降低與毛細結構 200中逆向回流冷凝液的交互作用機會。另外，由於#★,旱], for the day guard, through the acceleration of the nozzle 300, it can be transmitted to the condensation section more quickly_cooling and releasing heat. ^The development status of the straight hot steam flow field can clearly show that the high-speed f-steam will rush to the cold f sub-stage and diffuse toward the tube wall at a higher speed after the small nozzle is ejected, and the lateral diffusion speed and steam The speed is inversely proportional. If the main stream vel〇clty is faster, it shows that the axial distance before the steam is ejected from the small orifice of the nozzle and spread laterally to the wall of the contact tube, that is, the steam flow is in the The distance within the distance will greatly reduce the chance of interaction with the reverse reflux condensate in the capillary structure 200. In addition, due to
瘵A被喷嘴300加速，其流動速度較未設置噴嘴3〇〇 時快，加之喷冑300之漸縮效應，從❿蒸汽向周圍擴 散之機會減小，大量蒸汽通過蒸汽通道徑直地流向冷 凝段600，因此，噴嘴3⑻之設置還可降低蒸汽流與 毛細結構2GG介面之交互干擾’防止蒸汽傳輸過程中 因熱望之散失而提早發生冷凝現象所造成對傳輸中 之瘵汽流阻加大之負面效應，並使加速之蒸汽提早到 達冷凝段。由於蒸Ά流與毛細結構2〇〇介面之交互干 11 1292470 ' 擾降低，冷凝液回流到蒸發段400更爲順暢，達到降 低熱阻及提升熱管最大傳熱能力之功效。 圖2爲本發明熱管之第二實施例之剖面示意圖。 ' 該熱管與第一實施例之區別在於：本實施例之直型熱 管，其蒸發段400在中間冷凝段600在兩端，絕熱段 500位於蒸發段400和冷凝段600之間。在蒸汽通道 中接近蒸發段400與絕熱段500之邊界分別設置一朝 鲁 向冷凝段600之喷嘴300，但該喷嘴300之位置不限 於此，亦可設置于絕熱段500上。與第一實施例同理， 當蒸發段400將吸收外界熱源之熱量傳給密封殼體 100内之工作液體使其蒸發，並分別通過該喷嘴300 之加速作用，可使蒸汽流更快速傳輸到兩端之冷凝段 600冷卻並釋出熱量，且可降低蒸汽流與毛細結構2〇〇 介面之交互干擾，使冷凝液回流到蒸發段4〇〇更爲順 暢，達到降低熱阻及提升熱管最大傳熱能力之功效。 φ 圖3爲本發明熱管之第三實施例之剖面示意圖； 該熱管與第二實施例之區別在於：本實施例將第二實 施例之直型熱管折彎使其呈U型，其蒸發段400在中 間冷凝段600在兩端，連接蒸發段4〇〇與冷凝段600 之彎折區爲絕熱段500。在蒸汽通道中接近蒸發段4 〇 〇 與絕熱段500之邊界分別設置一朝向冷凝段6〇〇之喷 嘴300，但該喷嘴300之位置不限於此，亦可設置于 絕熱段500上，如圖4所示。與第一實施例同理，當 1292470 • 蒸發段400將吸收外界熱源之熱量傳給密封殼體loo 内之工作液體使其蒸發，並分別通過該喷嘴300之加 速作用，可使蒸汽流更快速傳輸到兩端之冷凝段600 冷卻並釋出熱量，由圖3的流場發展700可明確的看 出高速蒸汽自噴嘴300小口射出後將以更高的速度向 前衝，進而將蒸汽快速流向冷凝段600，並同時向管 壁方向擴散，由於蒸汽由噴嘴300小口擴散到達彎管 φ 壁時的軸向距離很短，以致本發明因在U形熱管的蒸 發段400與絕熱段500界面附近安裝喷嘴3〇〇而具有 較習知同形熱管更長的不受界面干擾區，且可降低蒸 汽流與毛細結構介面之交互干擾，使冷凝液回流到蒸 發段400更爲順暢，同樣可達到降低熱阻及提升熱管 最大傳熱能力之功效。 綜上所述’在熱管之蒸汽通道中接近蒸發段4〇〇 與絕熱段500之邊界至少設置一朝向冷凝段6〇〇之喷 • 嘴300，該喷嘴30〇亦可設置于絕熱段500上。當蒸 發段400將吸收外界熱源之熱量傳給密封殼體1〇〇内 之工作液體使其蒸發，並通過該喷嘴3〇〇之加速作 用，可使瘵>飞流更快速傳輸到冷凝段6〇〇冷卻並釋出 熱置，且可降低瘵汽流與毛細結構2〇〇介面之交互干 擾，使冷凝液回流到蒸發段伽更爲順暢，從而達到 降低熱阻及提升熱管最大傳熱能力之功效。 綜上所述，本發明符合發明專利要件，爰依法提 13 1292470 出專利申請。惟，以上所述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係本發明熱管之第一實施例之剖面示意圖。 圖2係本發明熱管之第二實施例之剖面示意圖。 圖3係本發明熱管之第三實施例之剖面示意圖。 圖4係本發明熱管之第四實施例之剖面示意圖。 【主要元件符號說明】 密封殼體 100 底部 120 封口 140 毛細結構 200 喷嘴 300 蒸發段 400 絕熱段 500 冷凝段 600 流場發展 700 14瘵A is accelerated by the nozzle 300, and its flow speed is faster than when the nozzle 3 is not provided. In addition, the gradual effect of the squirt 300 reduces the chance of diffusion from the turbulent steam to the surroundings, and a large amount of steam flows straight through the steam passage to the condensing section. 600, therefore, the setting of the nozzle 3 (8) can also reduce the cross-interference between the steam flow and the 2GG interface of the capillary structure, which prevents the condensation caused by the early loss of condensation due to the loss of heat during the steam transmission process, which is negative for the increase of the turbulent flow resistance during the transmission. Effect and accelerate the accelerated steam to the condensation section. Due to the interaction between the evaporating turbulent flow and the capillary structure 2 1292470 'the disturbance is reduced, the condensate returns to the evaporating section 400 more smoothly, achieving the effect of reducing the thermal resistance and improving the maximum heat transfer capacity of the heat pipe. 2 is a schematic cross-sectional view showing a second embodiment of the heat pipe of the present invention. The heat pipe differs from the first embodiment in that the straight heat pipe of this embodiment has an evaporation section 400 at both ends of the intermediate condensation section 600, and an adiabatic section 500 is located between the evaporation section 400 and the condensation section 600. A nozzle 300 facing the condensing section 600 is disposed adjacent to the boundary between the evaporation section 400 and the adiabatic section 500 in the steam passage, but the position of the nozzle 300 is not limited thereto, and may be disposed on the adiabatic section 500. In the same manner as the first embodiment, when the evaporation section 400 transfers the heat of the external heat source to the working liquid in the sealed casing 100 to evaporate, and through the acceleration of the nozzle 300, the steam flow can be transmitted to the steam stream more quickly. The condensation section 600 at both ends cools and releases heat, and can reduce the interaction between the steam flow and the capillary structure 2, so that the condensate is returned to the evaporation section 4, which is smoother, reducing the thermal resistance and increasing the maximum heat pipe. The effect of heat transfer capacity. 3 is a schematic cross-sectional view of a third embodiment of the heat pipe of the present invention; the heat pipe is different from the second embodiment in that: the present embodiment bends the straight heat pipe of the second embodiment into a U-shape, and the evaporation section thereof 400 is at the both ends of the intermediate condensation section 600, and the bending zone connecting the evaporation section 4〇〇 and the condensation section 600 is the adiabatic section 500. In the steam passage, a nozzle 300 facing the condensation section 6 is disposed near the boundary between the evaporation section 4 and the adiabatic section 500. However, the position of the nozzle 300 is not limited thereto, and may be disposed on the heat insulation section 500, as shown in the figure. 4 is shown. Similarly to the first embodiment, when the 1292470 • evaporation section 400 transfers the heat of the external heat source to the working liquid in the sealed casing loo to evaporate, and through the acceleration of the nozzle 300, the steam flow can be made faster. The condensation section 600 transmitted to both ends cools and releases heat. It can be clearly seen from the flow field development 700 of Fig. 3 that the high velocity steam will be forwarded at a higher speed after being ejected from the nozzle 300, thereby rapidly flowing the steam. Condensation section 600, and simultaneously diffusing toward the wall of the tube, the axial distance due to the diffusion of steam from the small opening of the nozzle 300 to the wall of the bend φ is short, so that the present invention is near the interface between the evaporation section 400 and the adiabatic section 500 of the U-shaped heat pipe. The nozzle 3 is installed to have a longer interface interference zone than the conventional heat pipe, and the interaction between the steam flow and the capillary structure interface can be reduced, and the condensate is returned to the evaporation section 400 more smoothly, and the same can be achieved. Thermal resistance and the ability to increase the maximum heat transfer capacity of the heat pipe. In summary, at least a spray nozzle 300 facing the condensation section 6 is disposed in the steam passage of the heat pipe near the boundary between the evaporation section 4 and the heat insulation section 500. The nozzle 30〇 may also be disposed on the heat insulation section 500. . When the evaporation section 400 transfers the heat of the external heat source to the working liquid in the sealed casing 1 to evaporate, and through the acceleration of the nozzle 3, the 瘵> fly stream can be transmitted to the condensation section more quickly. 6〇〇cooling and releasing the hot set, and can reduce the interaction between the turbulent steam flow and the capillary structure 2 , interface, so that the condensate is returned to the evaporation section and the gamma is smoother, thereby reducing the thermal resistance and improving the maximum heat transfer of the heat pipe. The power of ability. In summary, the present invention complies with the requirements of the invention patent, and the patent application is filed according to law 13 1292470. However, the above description is only the preferred embodiment of the present invention, and equivalent modifications or variations made by those skilled in the art of the present invention should be included in the following claims. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic cross-sectional view showing a first embodiment of a heat pipe according to the present invention. Figure 2 is a schematic cross-sectional view showing a second embodiment of the heat pipe of the present invention. Figure 3 is a schematic cross-sectional view showing a third embodiment of the heat pipe of the present invention. Figure 4 is a cross-sectional view showing a fourth embodiment of the heat pipe of the present invention. [Main component symbol description] Sealed housing 100 Bottom 120 Seal 140 Capillary structure 200 Nozzle 300 Evaporation section 400 Adiabatic section 500 Condensation section 600 Flow field development 700 14