1252131 九、發明說明： 【發明所屬之技術領域】 本發明係關於該液體霧化裝置，且其可用於滅火系統、 衛生工程、液體燃料燃燒裝置及灌溉單元等。 【先前技術】 各種類型之液體霧化器已為吾人所熟知。舉例言之，從 專利RU20363 81 C1可知一液體霧化裝置，該裝置包括一喷 嘴及一***構件，其中該構件具有一與一喷嘴之一出口發 散通道部分軸向對齊之中心收斂圓錐孔（Ru 2〇336381cl、 IPC F23D 11/34、B05 B17/06 ’ 1995年 5 月 27 日頒予）。該裝 置進一步包括一適宜於該***構件相對於該喷嘴通道之該 出口部分軸向移動的元件。該***構件位於一與該喷嘴通 道軸向對準之圓柱形室内。 在一環形共振腔（其位於該***構件之一輸出端部與該 噴鳴出口通道之一端部之間的圓柱形室内）内，將一恒壓轉 變為一變壓。在該***構件移動時，該環形共振腔之體積 發生變化，從而使得液體壓力變化之頻率也相應改變。此 導致產生一脈動液流，其中該脈動液流之產生可促進液體 之有效霧化及細小霧化氣滴喷流之形成。藉由在一主流周 圍產生一系列較小直徑之環狀流而為該液流霧化提供另一 附加效果，該等環狀流係藉由自該噴嘴通道經由另外喷嘴 頭提供一部分液流而產生。 吾人所熟知之具體實施例之應用顯著提高了液流之霧化 效率，而能量消耗則有利地得以減少。然而，由於從外界 101155.doc 1252131 將空氣吸入該喷嘴通道表面與一發射液流間之空間中，並 進一步進入該共振腔中，因此該先前技術之裝置減小了該 流體之動&。@且應該指出，錢穴效應相λ，單相流體 中所採用之共振效應產生霧化液體喷霧之效率更低。 因此，先别技術之裝置無法提供所希望之液體霧化製程 之分散度變化範圍，即該液體霧化製程之分散度範圍在長 距離大分散度部分與中等距離細小霧化氣滴喷流之間。1252131 IX. Description of the Invention: [Technical Field] The present invention relates to the liquid atomizing device, and is applicable to a fire extinguishing system, a sanitary engineering, a liquid fuel burning device, an irrigation unit, and the like. [Prior Art] Various types of liquid atomizers are known to us. For example, a liquid atomizing device is known from the patent RU 20 363 81 C1, which comprises a nozzle and an insert member, wherein the member has a central converging conical bore axially aligned with an outlet diverging passage portion of a nozzle (Ru 2〇336381cl, IPC F23D 11/34, B05 B17/06 'granted on May 27, 1995). The apparatus further includes an element adapted to move axially relative to the outlet portion of the nozzle passage. The insert member is located in a cylindrical chamber axially aligned with the nozzle passage. In a ring resonator (which is located in a cylindrical chamber between the output end of one of the insert members and one of the ends of the sounding outlet passage), a constant pressure is converted into a variable pressure. As the insert member moves, the volume of the annular resonant cavity changes, causing the frequency of liquid pressure changes to change accordingly. This results in a pulsating fluid flow which promotes efficient atomization of the liquid and formation of a fine atomized gas droplet jet. Another additional effect is provided for atomization of the liquid stream by creating a series of annular streams of smaller diameter around a main stream that provide a portion of the liquid stream from the nozzle passage via the additional nozzle tip. produce. The application of the specific embodiments well known to us significantly increases the atomization efficiency of the liquid stream, while the energy consumption is advantageously reduced. However, since air is drawn from the outside 101155.doc 1252131 into the space between the nozzle channel surface and an emitter stream and further into the cavity, the prior art device reduces the movement of the fluid. @And it should be noted that the money point effect phase λ, the resonance effect used in single-phase fluids, produces atomized liquid sprays with lower efficiency. Therefore, the prior art device cannot provide the desired range of dispersion of the liquid atomization process, that is, the dispersion range of the liquid atomization process is in the long-distance large-distribution portion and the medium-distance fine atomized gas droplet jet. between.
自專利 US4013228(IPC-2 Β05Β1/30, 1977年 3 月 22 日頒予） 中可知-液體霧化裝置，該液體霧化裝置包括一具有一通 道之噴嘴，而該通道包含—圓柱形部分。該霧化器包含一 安置於該噴嘴圓柱形部分出口端之室中。在該室之—圓錐 形端壁上另有-具有出口圓柱形通道之噴嘴。具有該出口 通道之6亥至之該端壁係藉由一套管之位移而沿轴向移動， 其中該套管與該裝置之該主喷嘴係呈同軸對準關係。在該 具有圓錐形壁之套管内表面與該喷嘴套管的外表面之間所 界定之若干縱向通道係適合於將空氣自外界吸入室腔内， 而該室腔係位於該喷嘴之該出口圓柱形部分區域與具有該 出口圓柱形孔之圓錐形壁之間。 藉由提供-具有該圓錐形壁之套管一軸向位移，即可改 變-產生於該出口圓柱形通道出D端之霧化喷流的特徵。 根據該套管之不同位置，該喷嘴之圓柱形通道出口端的液 流發散部分係與該室之内圓錐表面（距離該噴嘴通道部分 最遠處)相碰撞，或與該套管之該圓錐形壁中該圓柱形通道 之内表面（距離該喷嘴通道部分最近處）相碰撞。 101155.doc 1252131 該前述裝置可產生預定特性在期望參數範圍内之霧化液 體喷流。然而，由於將空氣自外界吸入該等縱向通道（狹縫） 時會損失動能’所以使用此一裝置存在該液流動能減小之 相關問題。此外，先前技術之裝置無法將所產生之霧化喷 流之分散度調節至一期望範圍内。A liquid atomizing device comprising a nozzle having a passage and a cylindrical portion is known from the patent US Pat. No. 4,013,228 (issued to A.S. Pat. The atomizer includes a chamber disposed at the outlet end of the cylindrical portion of the nozzle. Also on the conical end wall of the chamber is a nozzle having an outlet cylindrical passage. The end wall having the outlet passage is moved axially by displacement of a sleeve, wherein the sleeve is in coaxial alignment with the main nozzle of the apparatus. A plurality of longitudinal passages defined between the inner surface of the sleeve having the conical wall and the outer surface of the nozzle sleeve are adapted to draw air from the outside into the chamber, and the chamber is located in the outlet cylinder of the nozzle The shaped partial region is between the conical wall having the cylindrical bore of the outlet. By providing an axial displacement of the sleeve having the conical wall, it is possible to change the characteristics of the atomizing jet produced at the D end of the outlet cylindrical passage. Depending on the position of the sleeve, the flow diverging portion of the cylindrical passage exit end of the nozzle collides with the inner conical surface of the chamber (the farthest from the nozzle passage portion), or the conical shape of the sleeve The inner surface of the cylindrical passage in the wall (the closest to the portion of the nozzle passage) collides. 101155.doc 1252131 The foregoing apparatus can produce an atomized liquid jet having a predetermined characteristic within a desired parameter range. However, since the kinetic energy is lost when air is drawn into the longitudinal passages (slits) from the outside, there is a problem associated with the reduction of the flowability of the liquid using such a device. Furthermore, prior art devices are unable to adjust the dispersion of the resulting atomized jet to a desired range.
與所主張之本發明最相近之發明係專利US4779803 (IPC B05 B 1/26、B05 B1/34，1988年 10月 25 日頒予）所描述之一 液體霧化器。該霧化器包含一具有一通道（該通道包括一出 口圓柱形部分）之喷嘴、一具有與該喷嘴通道之出口圓柱形 部分軸向對齊之孔之平板，及一將該平板相對於該喷嘴之 出口端表面軸向移動之平板移動構件。該平板移動構件係 套凸耳（隔離物），該等凸耳係沿方位角相互間隔一預定距 離放置。5亥平板連接元件被固定於該喷嘴之外表面上以用 於與該喷嘴部分之該平板一起軸向移動。 4平板中所具有之邊孔之直徑係大於該喷嘴通道之該出 圓柱形邛刀的直徑至少丨〇倍。根據在距該喷嘴通道部分The invention most similar to the claimed invention is one of the liquid atomizers described in U.S. Patent No. 4,779, 983 (IPC B05 B 1/26, B05 B1/34, issued October 25, 1988). The atomizer includes a nozzle having a passage (the passage including an outlet cylindrical portion), a plate having a bore axially aligned with the cylindrical portion of the outlet of the nozzle passage, and a plate opposite the nozzle A plate moving member whose axial end surface is axially moved. The plate moving member is provided with lugs (spacers) which are spaced apart from each other by a predetermined distance along the azimuth angle. A 5 s flat connecting member is fixed to the outer surface of the nozzle for axial movement with the flat plate of the nozzle portion. The diameter of the side hole in the 4 plate is greater than the diameter of the cylindrical file of the nozzle channel by at least a factor of two. According to the portion of the nozzle channel
部分與該平板之間預先與空氣混合）沿 。當該液流（在該噴嘴 社該平板之孔邊緣流 101155.doc !252131 動時，該液流發生霧化且產生細小霧化氣滴噴流。 該平板之最遠位置可使空氣流在液流自該噴嘴通道噴出 -後立即被吸入該液流中，並沿垂直於該喷嘴之對稱軸方向 促進該液流之旋轉。前述過程可增強霧化過程中該等液體 顆粒之踫撞強度，並促進該液體與該氣團混合，從而促使 ‘ 該等流體破裂成微滴。 應提及對於所考慮之先前技術應用，該液體之有效霧化 係藉由預先混合該液流與自外界吸入之空氣而實現。然 而々，此液體霧化方法與該液流之大量動能損失密切相關。 此等方法所導致之結果為該霧化液體喷流之流速減小，或 產生細小霧化氣滴噴流之能量損耗增加。 【發明内容】 本發明之一目的在於創造一種液體霧化器，該霧化器可 以最小此里扣耗產生具有不同霧化液流喷射錐角之細小霧 化氣滴喷流，同時該霧化液體喷流之強度高且均句性好。 鲁餘務組在於能夠控制霧化喷流之結構，且可將非霧化液 流轉變為具有最大發散角之細小霧化噴流。以上技術任務 之解決方案對-些霧化器之實際應用領域而言係重要的。 特定言之，該解決方案對各類火災場所之火災撲滅極端重 要舉例而〇，在期望將滅火化合物有效運送至非常遠之 地點時，以及需要借助於自近距離處射出受導向之細小霧 化水流噴射撲滅未撲滅之火災場所之情況下。 以上技術任務之解決方案與一技術成果之實現相關，該 技術成果包括減少產生一結構與形狀可控制之液體喷流所 101155.doc 1252131 消耗之能量。 既定技術成果係藉由實施—液體霧化器而實現，該液體 霧化器包括：一具有一通道之喷嘴，其中該通道包括-出 圓柱$。卩刀，#有—與該喷嘴通道之圓柱形部分 軸向對齊之孔之平板；及一適合相對於該喷嘴之一出口端 表面軸向移動該平板之平板移動構件。依照本發明，該平 板移動構件被設計成-與該嘴嘴轴向對齊放置之圓柱形套 管。該套管之内徑大於該噴嘴通道之出口圓柱形部分之直 私、&由至夕密封凡件將該套管之一端部連接至該噴嘴 上，該密封元件係提供該套管相對於該喷嘴轴向位移時氣 密地密封連接該套管與該噴嘴，該套管之一相對端部係與 固定於其上之平板結合以界定該套管端壁。該平板中之二 孔的直徑D係依據dsDsl.3d之條件選擇，其中d係該喷嘴通 道之該出口圓柱形部分的直徑。 本發明之上述本質特徵之組合可創造出藉由自該喷嘴喷 出^夜流堵塞該平板之孔，藉此中斷空氣自外界被吸入至 --至套^至）中，從而在該板所具之孔緊近鄰區域產生液 體氣穴沸騰的條件。 因此，借助於本發明的使用，將液流轉變為細小霧化氣 滴喷流之方法可藉由氣穴化製程得到，其中該氣穴化製程 與其他用於液體霧化之習知方法相比呈現最大之能量效 率。應指出的是，與上述效果相關聯之技術成果適用於產 生喷射液體喷流過程中所採用之〇.5〇购至5 Mpa之整個 液體壓力範圍。 I01155.doc -10- 1252131 藉由使具有該平板之該套管能夠相對於該噴嘴部分軸向 移動並按照本發明之申請專利範圍選擇該孔之大小，以該 平板之該出口孔之液流堵塞的效果得以獲得保證。該喷嘴 之出口端表面距該平板之最大距離可根據該喷嘴入口端之 液體壓力大小而變化。 在該霧化器結構之一較佳具體實施例中，其中藉由該套 管之軸向位移所提供該喷嘴之該出口端表面與該平板間之 最大間距不超過5 d，形成於該平板中之該孔之直徑〇係依 據d^D^Lld之條件選擇。 該喷嘴通道之該出口圓柱形部分的長度較佳係選在1 d 至5 d範圍内。一方面，該既定範圍係藉由形成一經精確導 向之液流所決定；另一方面，該既定範圍係藉由該噴嘴通 道中之最小液壓損失決定。 為減小由該喷嘴通道收斂所引起該喷嘴入口端之液壓損 失’該喷嘴具有一圓錐形或類圓錐形入口收斂部分。該既 定入口部分係與該出口圓柱形部分之入口相連接。 為進一步減小液壓損失，該霧化器可包括一與該喷嘴入 口端相通並且與該噴嘴通道軸向對齊放置之圓柱形室。該 圓柱形室之長度為該喷嘴通道入口孔直徑之5至2〇倍，且其 直徑與該喷嘴通道之該入口孔之直徑相等。 還建議鄰接至該孔邊緣之該平板部分的厚度係等於或小 於3d。在這種情況下，該液壓損失將減小，該液流所呈現 之氣穴霧化有效範圍更大。 【實施方式】 101155.doc -11- 1252131 該圖中所圖示説明之該液體霧化器係包括一具有一通道 之策嘴1 ’其中該通道包括—出σ圓柱形部分2與—圓錐形 入口收傲部分3。界定該圓錐部分3表面之圓錐頂角為3〇。。 該喷嘴收斂部分之頂角的最佳值係選在10。至50。之範圍 内其特彳政為該液流之液壓損失為最小。 在所考慮之本具體實施例之示例中，該喷之該圓柱形 部分2之長度為2d=1〇 mm，其中㈣麵係該喷嘴通道之該 出口圓柱形部分之直徑。該噴嘴】之該通道部分2之長度係 依據一較佳使用條件而作選取，因此該喷嘴之該圓柱：通 道出口部分之長度為1 d至5d。 該霧化器還包括一與該噴嘴丨軸向對齊之套管4。該套管4 係設計為可相對於該噴嘴！之該出口端表面進行轴向位 移。該套管4之端部與該喷嘴丨之間放置有一環形密封元件$ 以在該套管4相對於該噴嘴丨位移時能夠氣密地密封連接該 套管4與該噴嘴1。 位於該套管4之一相對端的是—平板，其中該平板具有一 與該噴嘴通道之該圓柱形部分2軸向對齊之出口孔6。該平 板界定該套管4之一端壁7，該套管大體上係用作一平板移 動構件。 该套官之該端壁7中孔之直徑〇為D=1 ·丨d，其中該噴嘴 通道之出口圓柱形部分2之直徑，即該直徑d可滿足條件 dsDsl.3 d。在與該開口 6邊緣鄰接之該區域中該端壁7之厚 度不超過3d，且在所考慮之本示例中，該厚度為12mm。 該套管4之該端壁7相對於該喷嘴〗之一端部表面8位移係 101155.doc •12- !252131 藉由一位移限制元件（以限制器9形成）所限制，該限制器9 係定位於該套管4之縱向狹縫1()中。自該喷嘴！之該端部表 面8至該套管4之該端壁7内表面的最大距離8為4 d以遵循 該套管4之一空腔丨丨之最佳尺寸。該套管4之内徑大於該噴 嘴通道之該出口圓柱形部分2之直徑d。 、 在所考慮之本發明具體實施例之示例中，該直徑^為$ mm，所以該霧化器套管之尺寸分別為：The part is mixed with the air in advance with the air). When the liquid flow (in the mouth of the nozzle, the flow edge of the plate is 101155.doc! 252131, the liquid flow is atomized and a fine atomizing gas droplet jet is generated. The farthest position of the flat plate allows the air to flow in the liquid The flow is ejected from the nozzle channel and is immediately drawn into the flow and promotes rotation of the flow along a direction perpendicular to the axis of symmetry of the nozzle. The foregoing process enhances the impact strength of the liquid particles during atomization. And promoting the mixing of the liquid with the air mass, thereby causing the fluid to break into droplets. It should be mentioned that for the prior art applications considered, the effective atomization of the liquid is by premixing the liquid stream and inhaling from the outside. This is achieved by air. However, this liquid atomization method is closely related to the large amount of kinetic energy loss of the liquid flow. The result of these methods is that the flow rate of the atomized liquid jet is reduced, or a fine atomizing gas droplet jet is generated. The energy loss is increased. SUMMARY OF THE INVENTION One object of the present invention is to create a liquid atomizer that can minimize the amount of spray cone angles of different atomized liquid streams. The gas droplets are sprayed, and the atomized liquid jet has high strength and uniformity. The Lu Yuwu group is capable of controlling the structure of the atomizing jet, and can convert the non-atomized liquid stream to have the largest divergence angle. The fine atomizing jet flow. The solution of the above technical tasks is important for the practical application fields of some atomizers. In particular, the solution is extremely important for fire extinguishing in various fire places. It is desirable to effectively transport the fire-extinguishing compound to a very remote location, as well as to spray a small atomized water stream directed from a close distance to extinguish an un-fired fire. The solution to the above technical tasks and a technical achievement Related to the implementation, the technical results include reducing the energy consumed to produce a structure and shape controllable liquid jet 101155.doc 1252131. The established technical results are achieved by implementing a liquid atomizer comprising : a nozzle having a passage, wherein the passage includes - an exit cylinder $. a rake, #有—axially aligned with a cylindrical portion of the nozzle passage a plate of the hole; and a plate moving member adapted to axially move the plate relative to an outlet end surface of the nozzle. According to the present invention, the plate moving member is designed to be cylindrically placed in axial alignment with the nozzle a sleeve having an inner diameter larger than a cylindrical portion of the outlet of the nozzle passage, and an end portion of the sleeve is connected to the nozzle by a sealing member, the sealing member providing the sleeve The tube is hermetically sealed to the sleeve and the nozzle when axially displaced relative to the nozzle, and one of the opposite ends of the sleeve is coupled to a plate secured thereto to define the sleeve end wall. The diameter D of the two holes is selected according to the conditions of dsDsl.3d, where d is the diameter of the cylindrical portion of the outlet of the nozzle passage. The combination of the above essential features of the present invention can be created by ejecting the night flow from the nozzle The hole of the plate is blocked, thereby interrupting the inhalation of air from the outside into the casing, thereby creating a condition of liquid cavitation boiling in the vicinity of the hole of the plate. Thus, by means of the use of the present invention, the method of converting a liquid stream into a fine atomized gas droplet jet can be obtained by a cavitation process, wherein the cavitation process is compatible with other conventional methods for liquid atomization. Than the greatest energy efficiency. It should be noted that the technical results associated with the above effects apply to the entire liquid pressure range used to produce 5 Mpa of the spray liquid jet. I01155.doc -10- 1252131 The flow of the orifice of the plate is selected by axially moving the sleeve with the plate relative to the nozzle portion and selecting the size of the hole in accordance with the scope of the invention. The effect of the blockage is guaranteed. The maximum distance of the outlet end surface of the nozzle from the plate may vary depending on the amount of liquid pressure at the inlet end of the nozzle. In a preferred embodiment of the atomizer structure, wherein the maximum distance between the outlet end surface of the nozzle and the flat plate provided by the axial displacement of the sleeve is not more than 5 d, formed on the flat plate The diameter of the hole in the hole is selected according to the condition of d^D^Lld. The length of the cylindrical portion of the outlet of the nozzle passage is preferably selected from the range of 1 d to 5 d. In one aspect, the predetermined range is determined by the formation of a precisely directed flow; on the other hand, the predetermined range is determined by the minimum hydraulic loss in the nozzle passage. To reduce the hydraulic loss at the inlet end of the nozzle caused by the convergence of the nozzle passage, the nozzle has a conical or conical-like inlet converging portion. The predetermined inlet portion is connected to the inlet of the cylindrical portion of the outlet. To further reduce hydraulic losses, the atomizer can include a cylindrical chamber that communicates with the nozzle inlet end and is axially aligned with the nozzle passage. The length of the cylindrical chamber is 5 to 2 times the diameter of the inlet opening of the nozzle passage, and the diameter thereof is equal to the diameter of the inlet opening of the nozzle passage. It is also suggested that the thickness of the flat portion adjacent to the edge of the hole is equal to or less than 3d. In this case, the hydraulic loss will be reduced and the cavitation atomization effective range exhibited by the flow will be greater. [Embodiment] 101155.doc -11- 1252131 The liquid atomizer illustrated in the figure includes a nozzle having a channel 1 'where the channel includes - a σ cylindrical portion 2 and a conical shape The entrance is proud of part 3. The conical apex angle defining the surface of the conical portion 3 is 3 〇. . The optimum value of the apex angle of the nozzle converging portion is selected to be 10. To 50. Within its scope, its special policy is to minimize the hydraulic loss of the liquid stream. In the example of the specific embodiment considered, the length of the cylindrical portion 2 to be sprayed is 2d = 1 mm, wherein the face is the diameter of the cylindrical portion of the outlet of the nozzle passage. The length of the channel portion 2 of the nozzle is selected according to a preferred use condition, so that the length of the cylinder: the outlet portion of the nozzle is from 1 d to 5 d. The atomizer also includes a sleeve 4 axially aligned with the nozzle. The sleeve 4 is designed to be relative to the nozzle! The outlet end surface is axially displaced. An annular sealing member $ is placed between the end of the sleeve 4 and the nozzle bore to hermetically seal the sleeve 4 and the nozzle 1 as the sleeve 4 is displaced relative to the nozzle. Located at the opposite end of the sleeve 4 is a flat plate having an exit aperture 6 axially aligned with the cylindrical portion 2 of the nozzle passage. The plate defines an end wall 7 of the sleeve 4 that is generally used as a plate moving member. The diameter 〇 of the hole in the end wall 7 of the sleeve is D = 1. 丨d, wherein the diameter of the cylindrical portion 2 of the outlet of the nozzle passage, that is, the diameter d satisfies the condition dsDsl.3d. The thickness of the end wall 7 in this region adjoining the edge of the opening 6 does not exceed 3d, and in the present example considered, the thickness is 12 mm. The end wall 7 of the sleeve 4 is displaced relative to one end surface 8 of the nozzle by a line 101155.doc • 12-!252131 which is limited by a displacement limiting element (formed by the limiter 9) which is Positioned in the longitudinal slit 1 () of the sleeve 4. From the nozzle! The maximum distance 8 from the end surface 8 to the inner surface of the end wall 7 of the sleeve 4 is 4 d to follow the optimum size of one of the sleeves 4 of the sleeve 4. The inner diameter of the sleeve 4 is larger than the diameter d of the outlet cylindrical portion 2 of the nozzle passage. In the example of a specific embodiment of the invention considered, the diameter ^ is $ mm, so the dimensions of the nebulizer sleeve are:
D=5.5釐米，S=10釐米 與該噴嘴1之該通道軸向對齊之圓柱形通道12係與該喷 嘴1之該通道圓錐形部分3之—入口端相連通。該圓柱形室 之直徑Dk等於該圓錐形部分3之—入口孔之直徑。根據^ 之最佳值範圍：5Dk^20Dk，該圓柱形室12之長度w ι〇 Dk d。 該液體霧化器按如下方式操作。 該液體霧化器被連接至一工作壓力為0 5撾1>3至1 Mpa之 供水管。開啓安裝於該供水f (該圖中未顯示）之—進水間 時’水被輸送至該用作-液流穩定器之該霧化器的該圓柱 形室12中。該流速在整個該室12之流動橫截面上是相等 的。然後該液體在該喷嘴丨之該通道的圓錐形部分3中加速 流動，然後被輸送至該噴嘴通道之該出口圓柱形部分2中， 其中形成一液流以進一步流入該套管4之一空腔1丨中。 當該套管4處於一產生細小霧化液體嘴流之位置時，該端 壁7與該喷们之該末端表面8間隔開。該套管锡軸向移 動，直至-自該圓柱形部分2之該出口孔噴出之發散液流衝 101155.doc -13- 1252131 擊該端壁7之該孔6的内表面爲止。該套管⑷在該噴嘴】之該 出口端表面8與該端壁7之該表面（其面對該出口端表面〇之 間移動的過程中，形成一由該套管4之該等壁界定之環形腔 11。該所產生之液流的喷射作用導致壓力減小。結果導致 空氣自外界經由該發散液流與該端壁7中該孔6之内表面間 所界定之間隔而被吸入該空腔丨丨中。 在該套管4移動過程中，該喷嘴丨與該套管4之連接係藉由 一環形密封元件5氣密地密封。 一旦該發散液流堵塞該孔6,中斷流入該空腔丨丨之空氣， 隨後該孔6被該液流完全堵塞。結果該空腔u中之靜壓急劇 下降，從而液體在與該孔6鄰接之區域發生氣穴沸騰。該既 定現象導致該實體液流***為液體微滴，隨後產生細小霧 化氣滴喷流。 當在與該孔6邊緣鄰接之該區域中該端壁的厚度不超過 3d，且因此該出口孔6之該通道長度不超過3(1時，經由該套 管4之該端壁7中所形成的出口孔6可在喷射欲霧化之液流 期間產生最小之液壓損失。 取決於該喷嘴1之通道之出口圓柱形部分2的直徑d，限定 該室之端壁7中所具孔6的直徑D : d^Dsl.3 d對在液體壓力 工作範圍内藉由該液流產生堵塞該平板之孔之效果是必要 條件。 實驗研究表明當該孔6之該直徑D超過1.3 d時，由於該孔 6沒有完全被液流部分堵住，空氣可無阻礙地自外界經過該 孔6滲入該空腔11，因而在該液體壓力之工作範圍内未顯露 101155.doc -14- 1252131 出堵塞該出口孔之效m由於重力使得該液流偏離該 孔6之一對稱軸而使得該液流撞上該套管4之該端壁7表面。 當無出現堵塞該出口孔的效果時，與該孔6鄰接之該區域 不發生液體氣穴沸騰，因而無法提供有效產生細小霧化液 體噴流之條件。在此情況下，僅當該液流自由流入環境介 質時才可發生液體霧化。然而由於摩擦力之作用，發生如 此一液體霧化過程所損耗之能量最大。 請注意將該直徑D增大至至少1>3 (!時，需大幅增加該液 體之工作壓力並且需增加該套管4之空腔長度。在這種情況 下’該套管之該空腔體積係相應增大，因此阻止該空腔中 產生所萬之低壓。缺乏所需之低壓，在與該出口孔鄰接之 該區域中，液體之氣穴沸騰效果實際上幾乎不會出現。因 此’該液流霧化之能量損耗可能不會明顯減小。 另一情況，當該出口孔之直徑D小於該喷嘴之該圓柱形通 道之直徑d時，由於以下原因，與該出口孔鄰接之該區域中 也無法顯現液體之氣穴沸騰效果。 由於該液流之截面超過該套管4之該端壁中該出口孔的 直徑D，在該液體開始流經該喷嘴1之該通道之該圓柱形部 分2的出口孔瞬間，該出口孔6完全為該液流所堵塞。在此 情況下，由於未自外界吸入空氣，該液流與該端壁7被阻隔 開’空氣被迫自該空腔11中擠出，且隨後液體填滿該空腔 11。因此該空腔11用作一升壓體積，液流自其中流出。在 此情況下，該液流之動能損失急劇增加，且該液流霧化之 效率降低。 101155.doc 1252131 所完成之該等實驗研究表明該液體霧化器結構尺寸之最 優條件為該孔6之直徑D符合條件：恢<ud。遵照該噴嘴 1之該出口端表面8與該端壁7之内表面間之最大距離s不超 過5 d之既定條件，可為结、、右 w務化之能量效率上獲得最佳 結果。 在所關心之本發明-具體實施例之示例中，採用具有長 度y之該出口圓柱形部分2的噴嘴通道可實現該液流 之最局動態穩Μ °如果該出口圓柱形部分2之長度更小， §亥液流不在穿過該喷嘴通道之整個通道截面時加速。這係 由於該液流自該通道壁分離，藉此而減小了噴嘴流量係 i：如果》亥圓柱形部分2之長度增加，藉由與該喷嘴通道壁 之摩擦力作用會致#^ i , 田致使動此知失增加。結果，自該喷嘴通道 之該出口孔噴出之液體的流速減小。 、措提，具有圓錐形或類圓錐形入口收傲部分3之喷嘴通 、σ實見亥液冰所旎達到之最大距離，從而實現該液流 之最大動能。一入口喷嘴通道之此形狀係接近於液體流線 形。 所考慮之本發明具體實施例之該示例中，一界定該通道 之該入口部分之圓錐的頂角係選在1〇。至5〇。範圍内。在該 指定錐角範圍内，w眘目（太 了貫現所產生之該氣滴喷流達到最大距 離。 依據該實驗之研究結果，已證實應用本發明所實現之液 體霧:器可以最小之能量損耗在整個流動截面中產生密度 及分散度均句之緻密且細小霧化液滴噴流。 I0ll55.doc -16- 1252131 本發明之工業應用 本杳月可用於滅火系統，尤其可用作背包式及可攜式滅 火裝置之一部分。本發明可進一步用作各種用途之處理設 備之一部分，也可用於濕潤環境及消毒劑及殺蟲劑之噴灑。 以上描述之利用本發明之示例為較佳示例，但其並未詳 細論述該附加申請專利範圍内之任何其他實施本發明之可 能性。透過使用熟諳此項技術者所熟知之設備與方法可實 現該等可能性。 只 【圖式簡單說明】 藉由該液體霧化器之-特定具體實施例及—附圖（圖〇 進一步舉例説明將要被頒予專利之本發明，該附圖（圖⑽ 描述該液體霧化H處於產线料流位㈣之縱向截面。 在該圖中該等虛線顯示該液體霧化器套管產生非霧化液流 過程之位置。該圖中之該等箭頭顯示該霧化器套管朝具有 該孔形成其中之該平板（該❹端壁）與該噴嘴端部表面接 觸之位置位移的方向。 【主要元件符號說明】 1 喷嘴 2 喷嘴通道之出口圓柱形部分 3 喷嘴通道之圓錐形入口收斂部分 4 套管 5 環形密封元件 6 出口孔 7 平板 101155.doc 1252131D = 5.5 cm, S = 10 cm The cylindrical passage 12 axially aligned with the passage of the nozzle 1 is in communication with the inlet end of the conical portion 3 of the nozzle 1. The diameter Dk of the cylindrical chamber is equal to the diameter of the inlet opening of the conical portion 3. According to the optimum value range of ^: 5Dk^20Dk, the length of the cylindrical chamber 12 is w ι〇 Dk d. The liquid atomizer operates as follows. The liquid atomizer is connected to a water supply pipe having a working pressure of 0 5 1 1 3 to 1 Mpa. When the water supply f (not shown in the drawing) is opened, the water is delivered to the cylindrical chamber 12 of the atomizer used as the liquid flow stabilizer. The flow rate is equal across the flow cross section of the chamber 12. The liquid then accelerates in the conical portion 3 of the passage of the nozzle and is then delivered to the outlet cylindrical portion 2 of the nozzle passage, wherein a flow is formed to further flow into a cavity of the sleeve 4. 1 丨. When the sleeve 4 is in a position to produce a flow of fine atomized liquid nozzles, the end wall 7 is spaced from the end surface 8 of the spray. The sleeve tin is moved axially until the diverging liquid jet ejected from the outlet opening of the cylindrical portion 2 strikes 101155.doc -13 - 1252131 against the inner surface of the hole 6 of the end wall 7. The sleeve (4) is formed by the wall of the end surface 8 of the nozzle and the surface of the end wall 7 (which faces the surface of the outlet end surface) The annular chamber 11. The injection of the generated liquid stream causes a decrease in pressure. As a result, air is drawn from the outside through the interval defined by the flow of the divergent liquid and the inner surface of the hole 6 in the end wall 7. During the movement of the sleeve 4, the connection of the nozzle 丨 to the sleeve 4 is hermetically sealed by an annular sealing member 5. Once the flow of the diverging liquid blocks the hole 6, the inflow is interrupted. The air in the cavity is entangled, and then the hole 6 is completely blocked by the liquid flow. As a result, the static pressure in the cavity u drops sharply, so that liquid boiling occurs in a region adjacent to the hole 6. This predetermined phenomenon causes The solid stream splits into liquid droplets, which in turn produces a fine atomizing droplet jet. The thickness of the end wall does not exceed 3d in this region adjacent the edge of the aperture 6, and thus the passage of the outlet aperture 6 When the length does not exceed 3 (1), the end wall 7 of the sleeve 4 is The resulting outlet opening 6 produces a minimum hydraulic loss during the injection of the liquid stream to be atomized. Depending on the diameter d of the outlet cylindrical portion 2 of the passage of the nozzle 1, the aperture 6 in the end wall 7 of the chamber is defined. The diameter D: d^Dsl.3 d is necessary for the effect of clogging the hole of the plate by the liquid flow in the working range of the liquid pressure. Experimental studies have shown that when the diameter D of the hole 6 exceeds 1.3 d, Since the hole 6 is not completely blocked by the liquid flow portion, the air can penetrate into the cavity 11 through the hole 6 without hindrance from the outside, and thus the liquid pressure is not revealed in the working range of the liquid pressure 101155.doc -14 - 1252131 The effect of the outlet hole m is caused by gravity to cause the liquid flow to deviate from the axis of symmetry of the hole 6 so that the liquid flow hits the surface of the end wall 7 of the sleeve 4. When there is no effect of blocking the outlet hole, The area adjacent to the hole 6 does not cause liquid cavitation boiling, and thus cannot provide a condition for effectively generating a fine atomized liquid jet. In this case, liquid atomization can occur only when the liquid flows freely into the environmental medium. Due to the effect of friction Such a liquid atomization process consumes the most energy. Please note that increasing the diameter D to at least 1 > 3 (!, the working pressure of the liquid needs to be greatly increased and the cavity length of the sleeve 4 needs to be increased. In this case, the cavity volume of the sleeve is correspondingly increased, thereby preventing the generation of a low pressure in the cavity. The required low pressure is lacking, and in the region adjacent to the outlet hole, the liquid gas The hole boiling effect is practically almost non-existent. Therefore, the energy loss of the liquid atomization may not be significantly reduced. In another case, when the diameter D of the outlet hole is smaller than the diameter d of the cylindrical passage of the nozzle The cavitation boiling effect of the liquid cannot be exhibited in the region adjacent to the exit hole for the following reason. Since the cross section of the liquid flow exceeds the diameter D of the outlet hole in the end wall of the sleeve 4, the liquid Immediately after the exit hole of the cylindrical portion 2 of the passage of the nozzle 1 is started, the outlet hole 6 is completely blocked by the liquid flow. In this case, since the air is not taken in from the outside, the liquid flow is blocked from the end wall 7. The air is forced to be extruded from the cavity 11, and then the liquid fills the cavity 11. The cavity 11 thus acts as a boosting volume from which the liquid flows. In this case, the kinetic energy loss of the liquid stream is drastically increased, and the efficiency of atomization of the liquid stream is lowered. 101155.doc 1252131 The experimental studies performed indicate that the optimum size of the structure of the liquid atomizer is that the diameter D of the hole 6 meets the condition: recovery <ud. According to the predetermined condition that the maximum distance s between the outlet end surface 8 of the nozzle 1 and the inner surface of the end wall 7 does not exceed 5 d, the best results can be obtained for the energy efficiency of the junction and the right side. In the example of the invention-specific embodiment of interest, the nozzle channel of the outlet cylindrical portion 2 having a length y can be used to achieve the most dynamic stability of the flow. If the length of the outlet cylindrical portion 2 is more Small, §Hail flow does not accelerate when passing through the entire passage section of the nozzle passage. This is because the liquid flow is separated from the channel wall, thereby reducing the nozzle flow rate i: if the length of the cylindrical portion 2 is increased, the frictional force with the nozzle channel wall will cause #^ i Tian Zhizhi made this increase. As a result, the flow rate of the liquid ejected from the outlet port of the nozzle passage is reduced. The nozzle has a conical or conical-shaped inlet, and the maximum distance of the liquid flow is achieved. This shape of an inlet nozzle passage is close to the liquid flow line shape. In this example of a particular embodiment of the invention contemplated, the apex angle of a cone defining the inlet portion of the passage is selected to be 1 〇. Up to 5 baht. Within the scope. Within the specified cone angle range, w is cautious (the gas droplet jet generated by the current reaches the maximum distance. According to the research results of the experiment, it has been confirmed that the liquid mist realized by the application of the invention can be minimized. The energy loss produces a dense and fine atomized droplet jet in the entire flow cross section. I0ll55.doc -16- 1252131 The industrial application of the present invention can be used in a fire extinguishing system, especially as a backpack type. And a part of a portable fire extinguishing device. The invention can be further used as part of a processing device for various purposes, and can also be used for a wet environment and spraying of a disinfectant and an insecticide. The above-described examples using the present invention are preferred examples. However, it does not discuss in detail any other possibility of implementing the invention within the scope of the appended claims. This possibility can be achieved by using equipment and methods well known to those skilled in the art. Only [schematic description] By way of a specific embodiment of the liquid atomizer and the accompanying drawings (which further illustrate the invention to be patented, the drawing Figure (10) depicts the longitudinal section of the liquid atomization H at the production line level (4). In the figure, the dashed lines show the position of the liquid atomizer casing to produce a non-atomized liquid flow process. The arrow indicates the direction in which the atomizer sleeve is displaced toward the position where the flat plate (the end wall) in which the hole is formed is in contact with the surface of the nozzle end. [Description of main components] 1 Nozzle 2 Outlet cylinder of the nozzle passage Conical portion 3 Conical inlet converging portion of the nozzle passage 4 Sleeve 5 Annular sealing member 6 Outlet hole 7 Plate 101155.doc 1252131
8 喷嘴1之端部表面 9 限制器 10 縱向狹縫 11 套管4之空腔 12 圓柱形通道 101155.doc -18-8 End surface of nozzle 1 9 Limiter 10 Longitudinal slit 11 Cavity of sleeve 4 12 Cylindrical channel 101155.doc -18-