200815681 九、發明說明： 【發明所屬之技術領域】 本發明係關於一種旋轉工具，尤其是，本發明關於 手持式旋轉工具或藉由安裝一機械產生加壓流體驅動 的旋轉工具。 【先前技術】 以傳統加壓流體驅動的旋轉工具，實際上施加於渦 輪機的流體壓力小於當流體進入旋轉工具時的流體壓 力。此壓力下降的原因基本上是由於加壓流體必須流經 由該旋轉工具的流體入口處至渦輪機的入口處的歪曲 路徑所致，且壓力下降的結果降低該旋轉工具的動力。 因此，對於加壓流體驅動的旋轉工具存在一需求為，減 少介於旋轉工具之入口處及渦輪機之入口處之間的壓 力下降，並藉以增加旋轉工具的動力。 【發明内容】 在一實施例中，本發明係有關於一旋轉裝置，該旋 轉裝置具有入口轉接器，用以連接旋轉裝置至加壓流體 源、渦輪轉子及輸入通道。該輸入通道位於入口轉接器 和渦輪轉子之間提供流體流通，且輸入通道具有靠近入 口轉接器之第一端部和自第一端部順流而下之開口，又 輸入通道具有介於第一端部和開口之一般固定的橫截 面之面積。 【實施方式】 200815681 請參閱第一圖，係根據本發明所顯示之旋轉工具 10。在此所描述之工具為一種具有藉由無油高壓氣體提 供動力之渴輪轉子之氣動工具，然而，吾人可知本發明 之概念可用於或適於任何具有任何型式之流體驅動馬 達之旋轉工具上，如：輪葉馬達；及藉由任何型式之壓 縮流體所提供動力之工具。 該旋轉工具10具有殼體13,該殼體13係由前部分 12和後部分14、轉子16、可轉動軸18以及消音殼體 46形成。 該殼體13之前部分12包括長筒狀之前侧元件24 和一短而擴大筒狀之後側元件28。該後侧元件28包括 外螺紋，用以响合該後部分14之内螺紋，如下所述， 俾使該前部分12連接至該後部分14。該前侧元件24 包括内螺紋，用以嚙合該固定螺帽30之外螺紋，如下 詳述。 該殼體13之後部分14具有流體入口部32、第一凸 緣34以及第二凸緣36，其中，該第一凸緣34係自該流 體入口部32之一端向外延伸，該第二凸緣36係自該第 一凸緣34之外緣向前延伸。該第二凸緣36之内表面係 形成内螺紋，用以嚙合該前部分12之後侧元件28之外 螺紋，俾使於其中形成一馬達腔室15。該流體入口部 32具有穿透其中之鑽孔38,該鑽孔38包含在該鑽孔38 一端之内螺紋以及相對該鑽孔38 —端之擴大反向鑽 孔，其中，該鑽孔38 —端之内螺紋係嚙合該入口轉接 器40之外螺紋。該第一凸緣34具有複數個孔45，用以 200815681 允許自該馬達腔室15排出流體以流動穿透該第一凸緣 34並流入該消音殼體46。密封環42固定於該反向鑽孔 且具有穿透於其中之鑽孔44，該鑽孔44與該後部分14 之流體入口部32之鑽孔38排列成行並使流體流通。 又，該密封環42可形成於該殼體13之後部分14的一 整體部分。 該消音殼體46包含後壁47以及自該後壁47向外 延伸之侧壁48，該後壁47與該侧壁48形成一腔室。該 後壁47具有一個或多個孔49,每一個孔49具有一預定 直徑，用以允許在該消音殼體46内之排出流體排出至 大氣中，且一貫穿其中心之鑽孔51用以接合該入口轉 接器40。該入口轉接器40延伸貫穿該後壁47且螺接(Q 該後部分14之流體入口部32，用以固定抵靠在該後部 分14之消音殼體46。形成於該消音殼體46之腔室内部 係消音材料26 ^該消音材料26係由類似s毛製品等材料 組成並適用於消除由排出流體所造成的噪音。 該入口，接器40適於接收來自於高壓空氣源之軟 管並具有允許流體流動穿透之鑽孔41。又，該入口轉接 器40可與該後部分14之流體入口部32的一部分一體 成型，且該消音殼體46可被牢固於該後部分14且穿透 其他裝置，例如：藉由直接地螺接消音殼體46於該殼 體13之後部分14。 可轉動軸18藉由後軸承組件20及前軸承組件21 而轉動地裝設在該殼體13之前部分12。該每一轴承組 件20、21之每一外輪係定位於該前部分12之前侧元件 200815681 24之每一端部之環狀反向鑽孔中，同時其内輪定位於 可轉動軸18上。該可轉動軸18具有突伸入該馬達腔二 15之後端，且耦合器70固定於該可轉動軸18之後二至 該耦合器70之前端接觸該後軸承組件2〇之内輪之二 部’俾使該後軸承組件20之内輪定位。固定螺帽3〇端 接入該前部分12之前側元件24之内螺紋並且接觸兮f 軸承組件21之外輪，俾使該前軸承組件21之== 位。该可轉動軸18具有向前突伸於該固定螺帽扣 端，且連接於筒夾22，該筒夾22用以固定一工星 ^ :)」：!如：研磨型工具。而習知技術的其它工且;二 方法亦可使用於本發明中。 /、固疋 =合H 70係由肢元件形成， 有 = 之前端中的第—鑽孔及在 ^^ 後端中的第二鑽孔74。兮筮_ 两口 σο 70之 後端，該第，、74二== 直徑地相對 ^第二觀74具有 搞合器7〇的外部，穿透 之環狀密封凸緣，該環灿六4俊°卩具有一向後延伸 7 4，用以密封職封環2 緣環繞於該第二鑽孔 體流動穿透流體人D部 ^②封的配置使得加壓流 器70至該徑向開口乃。°，密封環似而流入該耦合 其後端至鄰近其前• 11 7G外制纟t部分係從 該轉子16藉由螺接狀肩部76處。 設在該馬達腔室15内兔二輛合器之外螺紋上而裝 早使該轉子16於其中旋轉。在 200815681 此所述之該轉子16係一反動渦輪式轉子，如美國公告 號第4,776,752號之專利案，而該篇專利案與本發明係 同一申請人，藉由參考該案而進一步揭露本發明。然 而，本發明不受限於說明書中所舉實施例且可應用於具 有其它型式馬達之旋轉裝置。 在操作中，加壓空氣穿過該入口轉接器40流進該 旋轉工具10，其間加壓空氣流經該後部分14之流體入 口部32和該密封環42而流入至該耦合器70中之第二 鑽孔74，以及穿透該徑向開口 72而流入該轉子16。當 加壓空氣進入該轉子16時，加壓空氣進入第一環狀腔 室50,且流經穿透環狀壁60中之徑向孔54而環繞於彈 性閥環52，並進入至第二環狀腔室56，且導引流經喷 嘴58，藉以轉動該轉子16，並進而帶動該可轉動軸18 旋轉。加壓流體從該轉子16穿透該喷嘴58排出進入該 馬達腔室15，並穿透該殼體13之後部分14之孔45， 和穿透該消音材料26，加壓流體穿透該消音殼體46中 之孔46而離開該旋轉工具10而被排放至大氣之中。 當加壓流體被導引流入至該轉子16時，轉速便增 加至預定的最大值。作用於該彈性閥環52之離心力導 致該彈性閥環52產生徑向擴張，然而，該環狀壁60之 内表面除了該徑向孔54之外支撐該彈性閥環52。進而 使得該彈性閥環52之徑向擴張被導引入該徑向孔54， 以便於產生該彈性閥環52之控制的彈性變形量。當該 彈性閥環52變形時，該彈性閥環52接近該徑向孔54 之尾端。當距離充分地縮短時，流動穿透該徑向孔54 200815681 之流體將被限制且旋轉力亦減少。當作用於該系統之拖 曳力和旋轉力到達平衡時，作用於該彈性閥環52之作 用力亦將平衡，進而產生一固定的旋轉速度。如果拖曳 力增加的話，該平衡將瓦解，且作用於該彈性閥環52 的力將使得該彈性閥環52自其最接近該徑向孔54處縮 回’而允許額外流體流經直到另一平衡被建立。在任何 情況下，若該渦輪機超過欲控制速度，該彈性閥環52 將移動而進一步限制壓力流體，直到足夠之超速導致流 體停止，藉以導入超速安全性。 鑽孔38穿透該殼體13之後部分μ、鑽孔44穿透 該密封環42及第二鑽孔74穿透該耦合器70,以界定該 輸入通道穿透旋轉工具1〇,用以允許流體由該入口轉接 器40流動，穿透該徑向開口 72至該轉子16。該鑽孔 38、44、74具有近乎相同的橫截面，藉以允許流入該旋 轉工具10之流體穩定地穿透該旋轉工具10，並流入至 "亥後向開口 72而無需收縮或擴張之輸入通道。如此增 加了該旋轉工具10之動力。本發明之較佳實施例，該 鑽孔38、44、74係為筒形且其直徑約0.284英吋，且 其橫截面面積約〇·〇63平方英忖。 、 雖然本發明已以較佳實施例揭露如上，然其並非用 以限定本發明，任何熟悉此技藝者，在不脫離本發明之 精神和範圍内，當可作各種之更動與潤飾，因此，本發 %之保護範圍’當視後附之申請專利範圍所界定者為 準。 11 200815681 【圖式簡單說明】 第一圖顯示本發明旋轉工具之剖面圖。 【主要元件符號對照說明】 ίο—旋轉工具 12---前部分 13…殼體 14…後部分 15…馬達腔室 16…轉子 18—_可轉動轴 20—後轴承組件 21…前軸承組件 22—简失 24-—前侧元件 26— >肖音材料 28—-後側元件 30-—固定螺帽 32…流體入口部 34…第一凸緣 36---第二凸緣 38…鑽孔 40—入口轉接為 41…鑽孔 42…密封環 12 200815681 44— --鑽孔BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary tool, and more particularly to a hand-held rotary tool or a rotary tool driven by mounting a mechanically generated pressurized fluid. [Prior Art] A rotary tool driven by a conventional pressurized fluid actually has a fluid pressure applied to the turbine that is smaller than a fluid pressure when the fluid enters the rotary tool. The reason for this pressure drop is basically due to the fact that the pressurized fluid must flow through the tortuous path from the fluid inlet of the rotary tool to the inlet of the turbine, and the result of the pressure drop reduces the power of the rotary tool. Therefore, there is a need for a pressurized fluid driven rotary tool to reduce the pressure drop between the inlet of the rotary tool and the inlet of the turbine and thereby increase the power of the rotary tool. SUMMARY OF THE INVENTION In one embodiment, the present invention is directed to a rotating device having an inlet adapter for connecting a rotating device to a source of pressurized fluid, a turbine rotor, and an input passage. The input channel provides fluid communication between the inlet adapter and the turbine rotor, and the input channel has a first end adjacent the inlet adapter and an opening downstream from the first end, and the input channel has a The area of the generally fixed cross section of the end and the opening. [Embodiment] 200815681 Please refer to the first figure, which is a rotary tool 10 according to the present invention. The tool described herein is a pneumatic tool having a thirsty wheel rotor powered by oil-free high pressure gas, however, it will be appreciated that the concepts of the present invention can be applied to or adapted to any rotating tool having any type of fluid drive motor. Such as: vane motors; and tools powered by any type of compressed fluid. The rotary tool 10 has a housing 13 formed by a front portion 12 and a rear portion 14, a rotor 16, a rotatable shaft 18, and a muffler housing 46. The front portion 12 of the housing 13 includes a long cylindrical front side member 24 and a short enlarged cylindrical rear side member 28. The rear side member 28 includes external threads for engaging the internal threads of the rear portion 14, and the front portion 12 is coupled to the rear portion 14 as described below. The front side member 24 includes internal threads for engaging the external threads of the retaining nut 30, as described in more detail below. The rear portion 14 of the housing 13 has a fluid inlet portion 32, a first flange 34 and a second flange 36, wherein the first flange 34 extends outwardly from one end of the fluid inlet portion 32, the second projection The rim 36 extends forwardly from the outer edge of the first flange 34. The inner surface of the second flange 36 is internally threaded for engaging the outer portion of the rear portion 12 of the front portion 12 to form a motor chamber 15 therein. The fluid inlet portion 32 has a bore 38 therethrough, the bore 38 including an internal thread at one end of the bore 38 and an enlarged counter bore at the end of the bore 38, wherein the bore 38 is The internal thread of the end engages the external thread of the inlet adapter 40. The first flange 34 has a plurality of apertures 45 for allowing the fluid to escape from the motor chamber 15 to flow through the first flange 34 and into the muffler housing 46. A seal ring 42 is secured to the counterbored bore and has a bore 44 therethrough that is aligned with the bore 38 of the fluid inlet portion 32 of the rear portion 14 and circulates fluid. Also, the seal ring 42 can be formed in an integral portion of the portion 14 of the rear portion of the housing 13. The muffler housing 46 includes a rear wall 47 and a side wall 48 extending outwardly from the rear wall 47. The rear wall 47 and the side wall 48 define a chamber. The rear wall 47 has one or more apertures 49, each aperture 49 having a predetermined diameter for allowing exhaust fluid within the muffler housing 46 to be vented to the atmosphere, and a bore 51 extending through the center thereof for The inlet adapter 40 is engaged. The inlet adapter 40 extends through the rear wall 47 and is threaded (Q the fluid inlet portion 32 of the rear portion 14 for securing against the muffler housing 46 of the rear portion 14. The sound attenuating housing 46 is formed. The interior of the chamber is a sound absorbing material 26. The sound absorbing material 26 is composed of a material similar to s wool and is suitable for eliminating noise caused by the discharged fluid. The inlet, connector 40 is adapted to receive soft from a high pressure air source. The tube has a bore 41 that allows fluid flow to penetrate. Again, the inlet adapter 40 can be integrally formed with a portion of the fluid inlet portion 32 of the rear portion 14, and the sound attenuating housing 46 can be secured to the rear portion 14 and penetrating other means, for example, by directly screwing the muffler housing 46 to the rear portion 14 of the housing 13. The rotatable shaft 18 is rotatably mounted by the rear bearing assembly 20 and the front bearing assembly 21 The front portion 12 of the housing 13. Each of the outer gear trains of each of the bearing assemblies 20, 21 is positioned in an annular reverse bore of each end of the front side member 200815681 24 of the front portion 12 while the inner wheel is positioned Rotating on the shaft 18. The rotatable shaft 18 has a projection The motor cavity 2 is at the rear end of the motor, and the coupler 70 is fixed to the rotatable shaft 18, and the front end of the coupler 70 contacts the two ends of the inner bearing of the rear bearing assembly 2', so that the inner wheel of the rear bearing assembly 20 Positioning: The fixed nut 3 is inserted into the inner thread of the front side member 24 of the front portion 12 and contacts the outer wheel of the 兮f bearing assembly 21 to make the == position of the front bearing assembly 21. The rotatable shaft 18 has a direction The front protrusion protrudes from the fixing nut buckle end and is connected to the collet 22, and the collet 22 is used for fixing a working star ^:): such as: a grinding type tool. Other methods of the prior art can be used in the present invention. /, solid 疋 = H 70 is formed by the limb component, with = the first hole in the front end and the second hole 74 in the rear end of the ^^.兮筮 _ two ends σο 70 rear end, the first, 74 two == diameter relative to the second view 74 has the outer part of the fit 7 ,, penetrate the annular sealing flange, the ring can be six 4 4 The crucible has a rearward extension 74 for sealing the configuration of the seal ring 2 around the second bore body flow penetrating fluid body D such that the pressurizer 70 is to the radial opening. °, the seal ring flows into the coupling and its rear end is adjacent to its front • 11 7G outer 纟 t portion from the rotor 16 by the threaded shoulder 76. The rotor 16 is rotated in the motor chamber 15 by threading the outer shaft of the two couplings. The rotor 16 is a reverse-turbine-rotor rotor as described in the above-mentioned patent application No. 4,776,752, the entire disclosure of which is hereby incorporated by reference to . However, the present invention is not limited to the embodiments set forth in the specification and can be applied to a rotating device having other types of motors. In operation, pressurized air flows through the inlet adapter 40 into the rotary tool 10, during which pressurized air flows through the fluid inlet portion 32 of the rear portion 14 and the seal ring 42 into the coupler 70. The second bore 74 extends into the rotor 16 through the radial opening 72. When pressurized air enters the rotor 16, pressurized air enters the first annular chamber 50 and flows through the radial bore 54 in the annular wall 60 to surround the resilient valve ring 52 and into the second The annular chamber 56 is guided through the nozzle 58 to rotate the rotor 16 and thereby rotate the rotatable shaft 18. Pressurized fluid is discharged from the rotor 16 through the nozzle 58 into the motor chamber 15 and through the bore 45 of the portion 14 of the housing 13 and through the sound absorbing material 26 through which the pressurized fluid penetrates. The holes 46 in the body 46 exit the rotating tool 10 and are discharged into the atmosphere. When the pressurized fluid is introduced into the rotor 16, the rotational speed is increased to a predetermined maximum value. The centrifugal force acting on the resilient valve ring 52 causes the resilient valve ring 52 to expand radially, however, the inner surface of the annular wall 60 supports the resilient valve ring 52 in addition to the radial bore 54. Further, the radial expansion of the resilient valve ring 52 is introduced into the radial bore 54 to facilitate the controlled amount of elastic deformation of the resilient valve ring 52. When the resilient valve ring 52 is deformed, the resilient valve ring 52 approaches the trailing end of the radial bore 54. When the distance is sufficiently shortened, the fluid flowing through the radial bore 54 200815681 will be limited and the rotational force will also be reduced. When the drag force and the rotational force for the system reach equilibrium, the force acting on the elastic valve ring 52 will also be balanced, thereby producing a fixed rotational speed. If the drag force increases, the balance will collapse and the force acting on the elastomeric valve ring 52 will cause the elastomeric valve ring 52 to retract from its closest to the radial bore 54 while allowing additional fluid to flow through to another The balance is established. In any event, if the turbine exceeds the desired speed, the elastomeric valve ring 52 will move to further restrict the pressure fluid until sufficient overspeed causes the fluid to stop, thereby introducing overspeed safety. After the bore 38 penetrates the housing 13, a portion μ, the bore 44 penetrates the seal ring 42 and the second bore 74 penetrates the coupler 70 to define the input passage through the rotary tool 1 〇 to allow Fluid flows from the inlet adapter 40 through the radial opening 72 to the rotor 16. The bores 38, 44, 74 have nearly identical cross-sections to allow fluid flowing into the rotary tool 10 to stably penetrate the rotary tool 10 and flow into the "backward opening 72 without the need to contract or expand the input aisle. This increases the power of the rotary tool 10. In a preferred embodiment of the invention, the bores 38, 44, 74 are cylindrical and have a diameter of about 0.284 inches and have a cross-sectional area of about 平方 63 square inches. While the invention has been described above in terms of a preferred embodiment, it is not intended to limit the invention, and it is possible to make various changes and modifications without departing from the spirit and scope of the invention. The scope of protection of this issue is subject to the definition of the scope of the patent application. 11 200815681 [Simple description of the drawings] The first figure shows a cross-sectional view of the rotary tool of the present invention. [Main component symbol comparison description] ίο—Rotary tool 12---front portion 13...housing 14...rear portion 15...motor chamber 16...rotor 18--rotatable shaft 20-rear bearing assembly 21...front bearing assembly 22 - 失失24--front side member 26 - > audible material 28 - rear side member 30 - - fixing nut 32 ... fluid inlet portion 34 ... first flange 36 - second flange 38 ... drill Hole 40 - inlet transfer is 41... bore 42... seal ring 12 200815681 44 — -- drilling
45— 孑 L 46— >肖音殼體 47…後壁 48…侧壁 49—孔 50…第一環狀腔室 52…彈性閥環 54—徑向孑L 56…第二環狀腔室 58…喷嘴 60…環狀壁 70…耦合器 72…徑向開口 74…第二鑽孔 7 6—壞狀肩部45—孑L 46—> Xiaoyin housing 47...rear wall 48...side wall 49—hole 50...first annular chamber 52...elastic valve ring 54—radial 孑L 56...second annular chamber 58...nozzle 60...annular wall 70...coupler 72...radial opening 74...second bore 7 6—bad shoulder