201029910 六、發明說明： 【發明所屬之技術領域】 本發明係關於-種用&纺紗機或絞線機的纺鐘上的气 線之夾緊裝置，此夾緊裝置配置於一上紡錘部件上包含 -固定式夾緊元件及-軸向移動式夾緊元件；#向移動式 夾緊元件係藉由彈簧力而壓迫固定式夾緊元件，其中軸向 移動式夾緊元件可負載有球形離心力元件以一力對抗彈^ 力，此力將軸向移動式夾緊元件與固定式夾緊元件在轴向 上彼此分開，以此方式在兩者之間形成一夾緊間隙；而且 夾緊裝置具有在徑向上延伸的半殼體，這些半殼體係用以 配置並引導離心力元件，一個別的半殼體係配置於軸向移 動式夾緊元件上，而個別對應的半殼體則配置於—牢牢設 置的插座兀件上；軸向移動式夾緊元件的半殼體形成有相 對於水平方向傾斜的一連桿，而且，插座元件的對應半殼 體形成有大致平行於水平方向的一連桿。 【先前技術】 上述提到以離心力致動的此種夾緊裝置類型係揭示於 DE 1〇 2006 022 484 A1，其中下捲繞區域中的絲線圈小於 3 60度。為了能夠在落紗（d〇ffillg)之前達到確實夹緊，或者 在落紗之後絲線離心分離之前達到確實拼接（piecing)，該夾 緊裝置是由離心力所致動。根據DE 10 2006 022 484 A1中 所描述’軸向移動式夾緊元件的半殼體的連桿相對於水平 方向具有一傾斜角。以離心力致動的夾緊裝置中的連桿所 201029910 選擇的傾斜角，決定失緊裝置打開或關閉的極限旋轉速度 以便鬆開絲線並將絲線離心分離或夹緊。 在極限旋轉速度的範圍内’夾緊裝置的開啟與夾緊襄 置的關閉之間的過渡相當窄，致使夹緊裝置可能在纺鍾的 急速開始旋轉期間過早打開’如此一來將危及確實的拼 接。同理，當關閉夾緊裝置時，由於失緊裝置可能在纺鐘 減速期間過早關閉，而導致絲線並未夾緊或者在落紗過程 • 期間僅不恰當地固持住絲線。 【發明内容】 本發明之目的是要研發出一種夾緊裝置，其能夠將夾 緊裝置過早關閉或打開的風險降至最低。 此目的是根據藉由具有申請專利範圍帛i項所描述的 特徵之夾緊裝置的發明而達成。 此類型夾緊裝置的有利結構係描述於申請專利範圍的 ❹附屬項内。 根據申請專利範圍第丨項，相對於水平方向傾斜之移 動式夾緊元件的半殼體的連桿被建構成從移動式夾緊元件 的半殼體開始延伸於上紡錘部件的縱向，比起從插座元件 開始延伸於移動式夾緊元件的半殼體的方向來說，這些連 桿具有不同的傾斜角。連桿相對於水平方向傾斜之路線中 不同的傾斜角’導致開啟旋轉速度與關閉旋轉速度之間的 遲滯現象（hysteresis)的增加。換句話說，可以調整在開啟炎 緊裝置的旋轉速度範圍及關閉夾緊襞置的旋轉速度範圍之 5 201029910 間的間隔。由於連桿相對於水平方向傾斜的路線 同傾斜角的緣故，開啟夾緊裝置以鬆開夾緊間隙可被: 至高的旋轉速度。隨著紡鐘的急速開始旋轉有利 拼接及急速產生氣球狀鼓起，因為連桿相對於水平方向介 斜的路線中具有不同傾斜角之緣故，<緊裝置僅當旋轉= 度到達超過發生拼接且Μ拼接的旋轉速度時鬆開爽緊門 隙，以便離心分離夾緊的絲線。相反地，根據本發明，相 對於水平方向傾斜的連桿之結構料致夾緊裝置的關閉時 機被取代至低的旋轉速度至正好在紡錘處於停滯狀態 (standstill)之前，因此，產生一個這樣一個延長的時間窗 口，以便將絲線供應至,J《緊間陽：内，且在落紗過程之前確 實夾緊絲線。 為此，相對於水平方向傾斜之移動式夾緊元件的半殼 體的連桿可以具有徑向彎曲的路線。遲滯現象的增加是由 連桿路線中的不同曲率半徑所引起的。 作為另替代方式，相對於水平方向傾斜之移動式夾 緊元件的半殼體的連桿，在每一種情形下，可以被劃分為 第一部及第二部，第一部係從半殼體開始延伸在上紡錘部 件的縱軸方向上，而第二部係從插座元件開始延伸在移動 式夾緊元件的半殼體的方向上，第一部及第二部具有不同 的傾斜角。 第一部的傾斜應該要小於第二部的傾斜。在紡錘的加 速期間’第二部的傾斜角越大則會延遲在離心力元件的移 動式夾緊7L件上個別半殼體的到達，致使夾緊裝置僅能在 201029910 向旋轉速度下開啟。相較於先前技術，絲線被固持於夾緊 間隙内更長的時間《相反地，第一部的較小傾斜導致在紡 錘減速期間’離心力元件以一時間延遲到達插座元件上的 個別對應半殼體，致使夾緊元件的關閉以夾緊置於夾緊間 隙内的絲線可取代為低的旋轉速度。 較佳地’第一部的傾斜可以介於25度與35度之間。 特別地’第二部的傾斜可以介於45度與65度之間。 φ 黏滞阻尼媒介（viscous damping medium)可以有利地配 置於夾緊裝置中，此黏滞阻尼媒介可以是油或油脂，特別 是聚石夕氧油或油脂；由於其阻尼特性，可有助於額外地影 響夾緊裝置或離心力元件的移動順序。 黏滯阻尼媒介可以被配置於夾緊裝置的中間間隔内， 此等中間間隔係形成於移動式爽緊元件與固定式央緊元件 之間。因此，可以影響整個夾緊裝置的移動順序。 同樣地，黏滞阻尼媒介可以配置於半殼體内。在此變 _形例中，黏滯阻尼媒介係以針對性的方式影響離心力元件 的移動順序。 【實施方式】 圖1顯示紡織機（特別是紡 上纺鐘部件i。此上㈣料絞線機）的紡鐘的一 桿’此軸桿係用以容納一根管、根由金屬製成的轴 絲線而形成-管紗。為此，配置：上顯:二此管件上讓 紡紗環（spinning ring)(未顯示），.'、’邛件1上的疋 此纺紗環以同心方式圍繞 7 201029910 上紡錘部件1且其上繞行有一紡紗鋼絲圈（ring traveiia)， 此紡紗環使絲線偏向管件並捲繞於管件上。配置於上紡錘 部件1上的是-驅動錠盤（dHve wharve)2,在紡織機的操作 期間，可以藉由此驅動錠盤而驅動上纺錘部件1。 驅動錠盤2具有一裝配部14，係用以緊固本發明的夹 緊裝置4，以便在所產生的管紗的落紗產生期間夾緊絲線。 夾緊裝置4被離心力所致動，且可以採取兩個位置：一個 是如圖2所示的失緊位置，其中絲線是被夾緊，而另一個 是如圖3所示的開啟位置，在開啟位置時可以供應或鬆開 絲線且將絲線離心分離（centrifuged 。 圖2以剖面圖顯示本發明的夾緊裝置4處於夾緊位 置。夹緊裝置4被建構相對於其縱向軸線旋轉對稱，此夾 緊裝置4具有一固疋式夾緊元件5及一相對於固定是夾緊 元件5可移動之夾緊元件6。環形突起17係配置於固定式 夾緊元件5上，且其下表面正對著移動式夾緊元件6。如圖 2所示，‘夾緊裝置4處於關閉位置時，突起I?掷置於軸 向移動式夾緊元件6的一壓力面18上，此壓力面18較佳 地為圓錐狀，且其内表面正對著上紡錘部件丨，而軸向移動 式夹緊元件6的外側則遠離上紡錘部件丨。在夾緊位置中， 夾緊70件5與6的壓力面18及凸起17被擠壓而互相頂靠， 同時在開啟位置中，如圖3所示，在兩個夾緊元件5與6 之間產生一夾緊間隙16。夾緊裝置4是多件式部件且除固 定式夾緊元件5及軸向移動式夾緊元件6之外，夾緊裝置4 包含一插座元件7,其在夾緊裝置4的組裝位置中，此插座 201029910 疋件7可以被支撐於驅動焚盤2的一凸緣狀肩部⑺上以 •便在軸向Τ向上固定央緊裝置心插座元件7卡合於驅動錠 盤2的滾花3 (knurHng)，以防止夾緊裝置4的旋轉。被擠 麗於驅動錠盤2的裝配部Μ上的固定式夾緊元件5在 上固定住夾緊裝置4。 ° 而且，夹緊裝置4包含一壓縮彈菁8及複數個離心力 讀9,這些離心力元件9特別被建構成球形且均勻地分佈 參於上纺鐘部件1的周圍，且彼此偏移一角度，而且，這些 離心力元件9被配置成與夾緊裝置4中的夾緊間隙Μ隔開： 插座兀件7亦被用於容納並引導離心力元件$。為此， 大致呈圓柱形的插座元件7具有一壁體u，此壁體與上纺 錘部件1的縱向轴線同軸且設有多個通孔12 ; =應於離心力元件9的數量。配置於壁體:1的側邊2 12開二動:盤2的是半殼體13,這些半殼體13從通孔 此二 錘部件1的縱向轴線徑向朝外延伸。在 e 滑形中，半殼體13在轴向上毗連通孔ι2。 且右=實際上完全圍繞離心力M9’移動式夾緊元件6 、/體15在徑向傾斜方向上延伸且對應於半殼體13。 用於容納離心力元件9的车 力…力…的丰殼體13與15是依據球形離心 的形狀而成形’且適應其尺寸。 的引Si:件9於爽緊裝置4内的引導是由過-連桿狀 達成。為此，在每一情形中，移 的半殼移動式夾緊70件6 插座元件7具有相對於水平方向傾斜的—連桿⑼，而且， 7的半殼體13具有在徑向方向上延伸的-連桿 9 201029910 19 ’其中，球形離心力元件9可以在徑向上移動。 相對於水平方向傾斜之移動式夾緊元 劃分成-第一…一第二部22。在此情形中，；：： 21與第二部22具有不同的傾斜角，第一部^是從移 夾緊元件6的壁體開始延伸於纺錘i的縱向轴線方向，= 一部21㈣斜角小於第二部22的傾斜角，而第二部 是從移動式夾緊元件6正對著播座元件7的一側開始延伸 於半殼體13的方向。第m的傾斜角較佳地是介於。 度與35度之間，同時第二部22的傾斜角則介於μ度與μ 度之間。在夾緊裝i 4的周圍方向上呈對稱配置的半殼體 15之個別連桿20的第一部21與第二部22總是具有相同的 傾斜角’以達成同時引導並影響離心力元件9的移動， 以避免夾緊裝置4内部的傾斜。 壓縮彈簧8係支撑於插座元件7上及圍繞插座元件7 的移動式夾緊元件6上，且於固定式夾緊元件5的方向擠 魔移動式夾緊元件6。夾緊裝置4的夾緊位置與開啟位置之 間的過渡是在到達-旋轉速度時發生，此旋轉速度是隨著 第°卩21與第二部22所選定的傾斜角呈函數變化。第二 部22的傾斜角越大，導致藉由離心力元件9到達移動式夹 緊元件6的半殼體13會在紡鍾加速時延遲。在將絲線爽緊 於夾緊間隙16内的期間，用以克服作用於夹緊元件5與6 上的彈簧力所需之離心力僅在一高開啟旋轉速度時達成， 此尚旋轉速度係例如位於大約8〇〇〇 1/min的範圍内。此旋 轉速度是大於拼接完成時的旋轉速度。結果是，確定用於 201029910 確實拼接的紡錘急速旋轉及絲線汽球的急速形成，並不會 使夾緊的絲線過早被離心力分離。相反地，相較於第二部 22來說，第一部21的傾斜角越小會導致在紡錘減速時開始 落紗過程且使與紡錘相連的絲線被夾緊；離心力元件9相 對於其等的移動順序受影響，以此方式只有在達到特定旋 轉速度遠小於開啟旋轉速度時，這些離心力元件9才可以 離開移動式夾緊元件6的個別半殼體丨3的位置。依據本發 明移動順序的影響，導致開啟旋轉速度與關閉旋轉速度之 間的遲滯現象增加。因此，由於離心力所引起以及防止夾 緊裝置4因為壓縮彈簧8的彈簧力而關閉的反作用力被維 持到一旋轉速度’例如大約2500 1/min至4000 i/min的範 圍之間。在紡錘處於停滞狀態之後，夾緊裝置4亦維持關 閉位置。開啟旋轉速度係根據在紡紗機上所欲處理的材料 特性而決定；換句話說，當處理較粗的紗線而非較細的紗 線時’此開啟旋轉速度會比較小。第一部2 1的傾斜及第二 φ 部22的傾斜被對應地選擇，以達成適合所處理的紗線之旋 轉速度。夾緊裝置4的開啟旋轉速度是關閉旋轉速度之至 少兩倍。 夾緊裝置4的開啟旋轉速度與關閉旋轉速度之間的遲 滞現象的影響’可能會進一步被其他結構性尺寸所影響。 為此，可改變離心力元件9的質量及/或壓縮彈簧8的彈簧 常數。同樣地’在連桿中使用阻尼媒介，例如油或油脂， 特別疋聚；ε夕氧油或聚石夕氧油脂，由於阻尼媒介的黏性這 些阻尼媒介可能會使離心力元件9的移動順序產生延遲， 11 201029910 如此有助於影響遲滯現象。 處於關閉位置或開啟位置的夾緊裝置4之另— 例顯示於圖4及圖5中。夾緊裝置4的第二實施例不同於 第-實施例之處在於：相對於水平方向傾斜之移動式夹緊 兀件6的連桿2G具有徑向彎曲的路線23，致使從移動式炎 緊元件6的半殼體15開始於上紡錘部件1的縱向軸線方 向：其具有-傾斜角不同於從插座元# 7開始於移動式夾 緊兀件6的半殼艘15的方向的傾斜角。連桿μ的徑向 曲路線23利用與上述第__實施例中相同的方式而影響離心 力元件9的移動順序，於是增加開啟旋轉速度與關閉旋轉 速度之間的遲滯現象。 【圖式簡單說明】 、下將藉由圖式令所顯示的實施例而詳細說明本發 明，其中： 圖1顯示一上紡錘部件的局部立體圖。 顯示本發明的夾緊裝置處於夾緊位置時的剖面圖。 圖3顯示夾緊裝置處於開啟位置時的剖面圖。 圖4顯不爽緊裝置的第二實施例處於夾緊位置時的剖 面圖。 圖5顯不夹緊裝置的第二實施例處於開啟位置時的剖 面圖。 【主要元件符號說明】 201029910201029910 VI. Description of the Invention: [Technical Field] The present invention relates to a gas line clamping device on a spinning clock of a spinning machine or a stranding machine, which is arranged on an upper spindle The component comprises a fixed clamping element and an axially movable clamping element; the #moving clamping element compresses the stationary clamping element by a spring force, wherein the axially movable clamping element can be loaded The spherical centrifugal force element resists the elastic force by a force which separates the axially movable clamping element from the fixed clamping element in the axial direction, thereby forming a clamping gap between the two; The tensioning device has a semi-shell extending radially, the half-shells for arranging and guiding the centrifugal force element, one of the other half-shells being arranged on the axially movable clamping element, and the respective corresponding half-shells being configured On the socket member that is firmly provided; the half-shell of the axially movable clamping member is formed with a link inclined with respect to the horizontal direction, and the corresponding half-shell of the socket member is formed substantially parallel to the horizontal direction a link. [Prior Art] The type of the above-mentioned type of clamping device which is actuated by centrifugal force is disclosed in DE 1〇 2006 022 484 A1, in which the wire coil in the lower winding region is less than 3 60 degrees. In order to be able to achieve a positive grip before the doffing, or to achieve a precise chipping before the centrifugation after the doffing, the clamping device is actuated by centrifugal force. The connecting rod of the half-shell of the axially movable clamping element described in DE 10 2006 022 484 A1 has an inclination angle with respect to the horizontal direction. The angle of inclination of the connecting rod in the centrifugally actuated clamping device 201029910 determines the ultimate rotational speed at which the detent device opens or closes in order to loosen the wire and centrifuge or clamp the wire. In the range of extreme rotational speeds, the transition between the opening of the clamping device and the closing of the clamping device is rather narrow, so that the clamping device may open prematurely during the rapid start of the spinning of the spinning clock. Splicing. Similarly, when the clamping device is closed, the wire may not be clamped during the deceleration of the spinning ring due to the premature closure of the spinning ring, or the wire may only be improperly held during the doffing process. SUMMARY OF THE INVENTION It is an object of the invention to develop a clamping device that minimizes the risk of premature closure or opening of the clamping device. This object is achieved in accordance with the invention of a clamping device having the features described in the scope of claim 帛i. Advantageous configurations of this type of clamping device are described in the dependent section of the patent application. According to the third aspect of the patent application, the connecting rod of the half-shell of the movable clamping element inclined with respect to the horizontal direction is constructed to extend from the half-shell of the movable clamping element to the longitudinal direction of the upper spindle member, as compared with These links have different inclination angles in terms of the direction in which the socket elements extend from the half-shell of the mobile clamping element. The different inclination angles of the links in which the links are inclined with respect to the horizontal direction cause an increase in hysteresis between the opening and closing speeds. In other words, it is possible to adjust the interval between the opening speed range of the opening device and the closing speed range of the clamping device 5 201029910. Due to the inclination of the connecting rod with respect to the horizontal direction and the inclination angle, the opening of the clamping device to release the clamping gap can be: a high rotational speed. With the rapid start of spinning of the spinning clock, it is advantageous for splicing and rapid generation of balloon-like bulging. Because the connecting rod has different inclination angles with respect to the horizontal oblique direction, the <tightening device only occurs when the rotation = degree exceeds the occurrence of splicing. And the splicing rotation speed loosens the tight door gap to centrifugally separate the clamped wire. In contrast, according to the present invention, the structure of the link inclined with respect to the horizontal direction causes the closing timing of the clamping device to be replaced to a low rotational speed just before the spindle is in a standstill, thus producing such a Extend the time window to supply the wire to, "Jinyang: Inside, and indeed clamp the wire before the doffing process. To this end, the connecting rod of the half-shell of the movable clamping element inclined with respect to the horizontal direction may have a radially curved path. The increase in hysteresis is caused by different radii of curvature in the link path. Alternatively, the connecting rod of the half-shell of the movable clamping element inclined with respect to the horizontal direction may be divided into a first portion and a second portion in each case, the first portion being a half-shell Initially extending in the direction of the longitudinal axis of the upper spindle member, the second portion extends from the socket member in the direction of the half-shell of the movable clamping member, the first portion and the second portion having different inclination angles. The inclination of the first portion should be smaller than the inclination of the second portion. During the acceleration of the spindle, the greater the inclination angle of the second portion delays the arrival of the individual half-shells on the movable clamping 7L of the centrifugal force element, so that the clamping device can only be opened at the rotational speed of 201029910. Compared to the prior art, the wire is held in the clamping gap for a longer period of time. Conversely, the smaller inclination of the first portion causes the centrifugal force element to reach the individual corresponding half-shell on the socket element with a time delay during spindle deceleration. The body, causing the closure of the clamping element to clamp the wire placed within the clamping gap, can be replaced by a low rotational speed. Preferably, the inclination of the first portion can be between 25 and 35 degrees. In particular, the inclination of the second portion may be between 45 and 65 degrees. Φ viscous damping medium can advantageously be arranged in the clamping device, the viscous damping medium can be oil or grease, especially polysulfate oil or grease; due to its damping characteristics, can help The order of movement of the clamping device or the centrifugal force element is additionally influenced. The viscous damping medium can be disposed in an intermediate space of the clamping device, the intermediate spaces being formed between the mobile cooling element and the stationary central locking element. Therefore, the order of movement of the entire clamping device can be affected. Likewise, the viscous damping medium can be disposed within the half-shell. In this variant, the viscous damping medium affects the order of movement of the centrifugal force elements in a targeted manner. [Embodiment] Figure 1 shows a spinning machine (especially a spinning bell component i. This upper (four) stranding machine) of a spinning rod is used to accommodate a tube, the root is made of metal The shaft wire forms a - cop. To this end, the configuration: the upper display: on the pipe, a spinning ring (not shown), the ', ' on the piece 1 of the spinning ring is concentrically surrounded by the spindle component 1 on the 201029910 and its There is a winding traveiia around the winding ring which deflects the wire towards the tube and is wound around the tube. Disposed on the upper spindle member 1 is a drive spindle (dHve wharve) 2, by which the upper spindle member 1 can be driven during the operation of the textile machine. The drive spindle 2 has a fitting portion 14 for fastening the clamping device 4 of the present invention to clamp the wire during the occurrence of the doffing of the produced spool. The clamping device 4 is actuated by centrifugal force and can take two positions: one is the untensioned position as shown in Figure 2, wherein the wire is clamped and the other is the open position as shown in Figure 3, The wire can be supplied or loosened and the wire can be centrifuged in the open position. Figure 2 shows in cross section the clamping device 4 of the present invention in a clamped position. The clamping device 4 is constructed to be rotationally symmetrical with respect to its longitudinal axis. The clamping device 4 has a fixed clamping element 5 and a clamping element 6 movable relative to the clamping element 5. The annular projection 17 is arranged on the stationary clamping element 5 and has a lower surface Opposite the movable clamping element 6. As shown in Fig. 2, when the clamping device 4 is in the closed position, the projection I is thrown onto a pressure surface 18 of the axially movable clamping element 6, this pressure surface 18 Preferably, the inner surface is opposite the upper spindle member, and the outer side of the axially movable clamping member 6 is away from the upper spindle member. In the clamped position, 70 pieces 5 and 6 are clamped. The pressure surface 18 and the projection 17 are pressed against each other while In the open position, as shown in Figure 3, a clamping gap 16 is created between the two clamping elements 5 and 6. The clamping device 4 is a multi-piece component and in addition to the stationary clamping element 5 and the axially movable In addition to the clamping element 6, the clamping device 4 comprises a socket element 7 which, in the assembled position of the clamping device 4, can be supported by a flange-like shoulder (7) for driving the burner disc 2 In order to prevent the rotation of the clamping device 4 from being engaged in the spindle plate 2, the core socket member 7 is engaged with the knurling gear 3 of the driving spindle 2 to prevent the rotation of the clamping device 4. The fixed clamping element 5 on the mounting portion is fixed to the clamping device 4. The clamping device 4 comprises a compression elastomer 8 and a plurality of centrifugal force readings 9, which are specially constructed to be spherical and Uniformly distributed around the upper spinning bell member 1 and offset from each other by an angle, and these centrifugal force members 9 are configured to be spaced apart from the clamping gaps in the clamping device 4: the socket member 7 is also used For accommodating and guiding the centrifugal force element $. For this purpose, the substantially cylindrical socket element 7 has a Body u, the wall body is coaxial with the longitudinal axis of the upper spindle member 1 and is provided with a plurality of through holes 12; = the number of centrifugal force members 9. The side walls 2 12 of the wall body 1 are open and movable: The disk 2 is a half-shell 13 which extends radially outward from the longitudinal axis of the two hammer members 1. In the e-slip, the half-shell 13 is axially adjacent to the hole ι2 And right=actually completely around the centrifugal force M9' the movable clamping element 6, the / body 15 extends in the radial oblique direction and corresponds to the half-shell 13. The force for accommodating the centrifugal force element 9... The housings 13 and 15 are shaped according to the shape of the spherical centrifugation and are adapted to their dimensions. The guiding of the Si:9 in the tightening device 4 is achieved by an over-link. To this end, in each case, the shifted half-shell mobile clamp 70 6-socket element 7 has a link (9) inclined with respect to the horizontal direction, and the half-shell 13 of 7 has a radial direction extension - Link 9 201029910 19 'In which the spherical centrifugal force element 9 can move in the radial direction. The movable clamping element that is inclined with respect to the horizontal direction is divided into a first portion - a second portion 22. In this case, ::: 21 has a different inclination angle from the second portion 22, and the first portion is extending from the wall of the displacement clamping member 6 in the longitudinal axis direction of the spindle i, = one portion 21 (four) The bevel angle is smaller than the inclination angle of the second portion 22, and the second portion is a direction extending from the side of the movable gripping member 6 facing the pod member 7 to the half-shell 13. The inclination angle of the mth is preferably between. The degree is between 35 degrees and the inclination angle of the second portion 22 is between μ and μ. The first portion 21 and the second portion 22 of the individual links 20 of the half-shell 15 which are symmetrically arranged in the circumferential direction of the clamping device 4 always have the same inclination angle 'to achieve simultaneous guiding and affecting the centrifugal force element 9 The movement is to avoid tilting of the inside of the clamping device 4. The compression spring 8 is supported on the socket member 7 and around the movable clamping member 6 of the socket member 7, and squeezes the movable clamping member 6 in the direction of the stationary clamping member 5. The transition between the clamped position and the open position of the clamping device 4 occurs at the arrival-rotation speed which varies as a function of the angle of inclination selected by the first 卩 21 and the second portion 22. The larger the inclination angle of the second portion 22, the lower the casing half 13 which reaches the movable clamping member 6 by the centrifugal force member 9 is delayed when the spinning clock is accelerated. During the tightening of the wire within the clamping gap 16, the centrifugal force required to overcome the spring force acting on the clamping elements 5 and 6 is achieved only at a high opening rotational speed, which is, for example, located Approximately 8〇〇〇1/min. This rotation speed is greater than the rotation speed at the completion of the splicing. As a result, it is determined that the rapid spin of the spindle and the rapid formation of the wire ball for the 201029910 do not splicing, and the clamped wire is not prematurely separated by centrifugal force. Conversely, the smaller the angle of inclination of the first portion 21 compared to the second portion 22, the more the doffing process begins when the spindle is decelerated and the wire connected to the spindle is clamped; the centrifugal force element 9 is relatively opposite thereto The sequence of movement is affected in such a way that the centrifugal force elements 9 can leave the position of the individual half-shells 3 of the movable clamping element 6 only when a certain rotational speed is reached which is much smaller than the opening rotational speed. According to the influence of the moving sequence of the present invention, the hysteresis between the opening rotational speed and the closing rotational speed is increased. Therefore, the reaction force due to the centrifugal force and the closing of the clamping device 4 due to the spring force of the compression spring 8 is maintained to a range of rotational speeds, e.g., approximately 2500 1/min to 4000 i/min. After the spindle is in a stagnant state, the clamping device 4 also maintains the closed position. The opening rotation speed is determined according to the characteristics of the material to be processed on the spinning machine; in other words, when the thicker yarn is processed instead of the finer yarn, the opening rotation speed is smaller. The inclination of the first portion 2 1 and the inclination of the second φ portion 22 are correspondingly selected to achieve a rotation speed suitable for the yarn to be processed. The opening rotational speed of the clamping device 4 is at least twice the closing rotational speed. The influence of the hysteresis between the opening rotational speed of the clamping device 4 and the closing rotational speed may be further affected by other structural dimensions. To this end, the mass of the centrifugal force element 9 and/or the spring constant of the compression spring 8 can be varied. Similarly, the use of damping media in the connecting rod, such as oil or grease, especially condensing; oxime oxygen or polysulfide grease, due to the viscosity of the damping medium, these damping media may cause the movement of the centrifugal force element 9 to occur sequentially. Delay, 11 201029910 This helps to influence the hysteresis. Another example of the clamping device 4 in the closed or open position is shown in Figures 4 and 5. The second embodiment of the clamping device 4 differs from the first embodiment in that the connecting rod 2G of the movable clamping jaw 6 inclined with respect to the horizontal direction has a radially curved path 23, resulting in a tight movement from the mobile The half-shell 15 of the element 6 starts in the direction of the longitudinal axis of the upper spindle part 1 : it has an inclination angle different from the direction of the half-hull 15 of the movable clamping jaw 6 starting from the socket element #7. The radial path 23 of the link μ affects the order of movement of the centrifugal force member 9 in the same manner as in the above-described embodiment, thereby increasing the hysteresis between the opening rotational speed and the closing rotational speed. BRIEF DESCRIPTION OF THE DRAWINGS The invention will be described in detail by way of embodiments shown in the drawings, in which: Figure 1 shows a partial perspective view of an upper spindle component. A cross-sectional view showing the clamping device of the present invention in a clamped position is shown. Figure 3 shows a cross-sectional view of the clamping device in the open position. Figure 4 is a cross-sectional view of the second embodiment of the unsweetened device in the clamped position. Figure 5 shows a cross-sectional view of the second embodiment of the clamping device in the open position. [Main component symbol description] 201029910
1 上紡錘部件 2 驅動錠盤 3 滾花 4 夾緊裝置 5 固定式夾緊元件 6 移動式夾緊元件 7 插座元件 8 壓縮彈簧 9 離心力元件 10 凸緣狀肩部 11 壁體 12 通孔 13 半殼體 14 裝配部 15 半殼體 16 夾緊間隙 17 環狀突起 18 壓力面 19 連桿 20 連桿 21 第一部 22 第二部 23 曲線路線 131 Upper spindle part 2 Drive spindle 3 Knurling 4 Clamping device 5 Fixed clamping element 6 Mobile clamping element 7 Socket element 8 Compression spring 9 Centrifugal force element 10 Flanged shoulder 11 Wall 12 Through hole 13 half Housing 14 Mounting part 15 Half-shell 16 Clamping gap 17 Annular projection 18 Pressure surface 19 Connecting rod 20 Connecting rod 21 First part 22 Second part 23 Curved route 13