5 經濟Α中央標率局員工消費合^杜印製 Α7 Β7 五、發明説明（i ) 本菜是關於一種黴测主軸拉刀力的最测儀及其應用測 最法*尤其是一種可结合在工具機做靜態或動態下皆可最 测主軸拉刀力的量测儀及其測最法。 主軸（Spindle〉是鉄床（Mi 11 ins Machine)等工具櫬 (Machine Tool)的重要組件之一，譬如在綜合加工機 (Machining Center » CNC>中，它是用來固定各種刀具 »並藉著快速轉動使切削工作具有充分的表面速度（Surfa -ce speed)來對被加工物進行切削加工。而主袖固定刀具 時，是利用拉刀機構提供的拉刀力（Tool clamping foree )來達成。因此若拉刀機構拉刀力不足或不穩定，除了會 降低軸切削時的剛性》亦會導致較低的切屑移除率（Chip removal rates)、較短的刀具薄命（Tool life)及振動（Vi -brations)等不良因素發生，影響加工效率及品質。習熟 工具機設計者皆知，拉刀機構的設計及拉刀力的決定是主 軸設計的重要關鍵之一。 拉刀力的大小涉及主軸及刀把材料、兩者配合狀況、 剛性問題及切削條件等因素》無論是對網珠或辦爪式等抓 刀機構等的設計，設計者在設計中會因前述各因素嫌機而 異，但一般是依據公式或經驗式來得知約略拉刀力的大小 。然而主軸設計後經製造完成當時獾得的實際拉刀（clai* -Ping)结果，或拉刀機嫌經長時間的操作使用後，拉刀力 是否能保捋一定而仍舊能達到所需的拉刀力及其剛性則無 法得知，因此，規副設計一客量測糸統，供賺時可量測工 具機的主軸拉刀力是必要的。 另一潛在的問趙則迄今無人注意並加Μ探索研究•即 -2 _ (請先閱讀背面之注意事項再填寫本頁) 本紙張尺度適用中國國家標準（CNS ) Α4規格（210Χ297公釐） 5 〇1S〇87 A7 B7 五、發明説明（2 ) 隨著主軸的轉速不斷提高的要求勢必使旋轉中主袖拉刀力 產生變化情形，使加工過程中拉刀力減低，而影響加工品 質。因此，本案的設計目的不僅期望可量測靜態拉刀力的 大<1、，亦進一步探索動態中的變，並可量測旋轉中主軸 拉73力的變化。 根據研究所知，拉刀力除了會改變刀把與主袖間斜錐 的靜摩擦力外，它尚有Μ下幾種效應： 1. 拉刀力會改變刀把受力_曲變形角度（deflection angle)，見於日本機械學會論文集C篇·昭52-7，第1050 -1058頁，拉刀力降低時，刀把的變形角度將增加•臀如 當拉刀力由4kN β華至lkN時，對BT30型刀把而言其彎曲角 度將倍增。 2. 拉刀力會改變刀把與主軸结合點的彎曲剛性（bending stiffness) » 隨著拉刀力的增加 * 彎曲剛性亦 _ 随著增 加。臀如40號刀把力由5kN谱加至15kN時，彎曲励T性約由 11N/ “ m增加至 13N/ “ m ° 3. 拉刀力會影響刀把结合點的動態特性，即拉力愈大 ，自然頻率（natura frequency)愈高，但阻尼比（damping ratio)會降低。 從許多文獻中發覺加大拉刀力具有穩定刀把切削性的 正面作用，然而拉刀力越大，繫刀力亦需越大’亦即仍有 負面作用。各種文獻的研究，多傾向於拉刀力變化對主軸 前述若干特性之影響*以協肋設計者決定最佳之拉刀力， 但對於實際探討拉刀機構在旋轉中拉刀力變化的文獻卻甚 _ 3 - 本紙張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） (請先閱讀背面之注意事項再填寫本頁) 装- Λ 經濟部^0央標準局員工消費合作24印製 5 經濟部P標準局員工消費合作製 Α7 Β7 五、發明説明（3 ) 可在靜態中悬測主軸拉刀力的發明，曾見於美國專利 第4,856,349號，其係利用在負載感測器（Load cell)内的 軸移位時，對負載感測器兩側產生的歷力加Μ感測，而轉 換顯示為拉刀力。 另一商品為德國UTILIS MUELLHEIM公司所設計生產之 軸拉力量測儀，為特點為模組化及數位顯示量測資料的設 計，對不同刀把規格的主軸亦提供適當的量測。其缺點為 僅提供靜態的拉刀力量測•對於旋轉中的主軸並無法提供 量測的能巧》而主軸旋轉是否對拉刀機構有其影響，甚而 是杏減低拉刀力大小皆為彼等所忽視。 拉刀力之量測，在量測裝置糸統設計的觀點上考處時 ，其困難點在於拉刀機構本身為旋轉體，其每分鐘轉速可 達數萬轉*若使用爾變規（strain gages)及測力儀來量測 拉刀力之方式，只可適用於靜態量測•但在動態量測過程 將使量測_號無法由外部接收，導致量測失效。為了達到 動態量測之目的，本案發明過程中曾考朧應用一種稱之為 滑環（slip rings)的裝置，使在旋轉的機件達成引接線之 連接•並利用電刷（brush)將旋轉訊號傳到外部的同定接點 。該構想曾經作過相當深度的探討，但基於構造和使用上 的複雜性•从及製造與維修成本上的考最，此一方式已放 棄。 本案的目的，在提供一種非接觸式晕測拉刀力的方法 〇 一 4 一 I--------------------r# — (請先閱讀背面之注意事項再填寫本頁) 訂5 Economy Alpha Central Bureau of Standards and Technology Staff Consumption ^ Du Printed Α7 Β7 V. Description of Invention (i) This dish is about a measuring instrument for measuring the broaching force of the spindle and its application method * especially a combination The measuring instrument and the method for measuring the spindle broaching force can be measured under the static or dynamic state of the machine tool. Spindle is one of the important components of Machine Tool such as Mi 11 ins Machine. For example, in the integrated machining machine (Machining Center »CNC>, it is used to fix various tools» and fast The rotation makes the cutting work have sufficient surface speed (Surfa-ce speed) to cut the workpiece. When the main sleeve is fixed to the tool, it is achieved by the tool clamping foree provided by the broaching mechanism. Therefore If the broaching force of the broaching mechanism is insufficient or unstable, in addition to reducing the rigidity of the shaft during cutting, it will also result in lower chip removal rates, shorter tool life and vibration (Vi -brations) and other unfavorable factors, which affect the processing efficiency and quality. Designers familiar with machine tools are well aware that the design of the broaching mechanism and the determination of the broaching force are one of the important keys in the design of the spindle. The size of the broaching force involves the spindle and Factors such as the material of the tool holder, the combination of the two, the rigidity problem and the cutting conditions. Whether the design of the mesh bead or claw type gripping mechanism, etc., the designer Various factors are different, but generally based on formulas or empirical formulas to know the approximate broaching force. However, the actual broach (clai * -Ping) result obtained by the badger after the design of the main shaft is manufactured, or the broaching machine is suspected. After a long period of operation, it is not known whether the broaching force can be maintained for a certain amount and the required broaching force and its rigidity can still be achieved. Therefore, the gauge design has a customer measurement system for profitability. It is necessary to measure the spindle broaching force of the machine tool. Another potential question is that Zhao Ze has not paid attention to it yet and added M to explore and research • namely -2 _ (please read the precautions on the back before filling this page) This paper size is applicable China National Standard (CNS) Α4 specification (210Χ297mm) 5 〇1S〇87 A7 B7 5. Description of invention (2) With the continuous increase of the speed of the main shaft, the force of the main sleeve broaching force in the rotation will inevitably change, so that The broaching force is reduced during the machining process, which affects the processing quality. Therefore, the design purpose of this case is not only to expect that the large static broaching force can be measured < 1, but also to further explore the changes in dynamics and measure the rotating spindle Pull 73 force According to the research, in addition to the broaching force will change the static friction between the knife handle and the main sleeve diagonal cone, it also has several effects: 1. The broaching force will change the force of the knife handle_deflection angle (deflection angle), see Chapter C of the Proceedings of the Japanese Society of Mechanical Engineering, Sho 52-7, pages 1050 -1058. When the broaching force is reduced, the deformation angle of the handle will increase. For the BT30 tool holder, the bending angle will be doubled. 2. The broaching force will change the bending stiffness of the junction between the tool holder and the spindle »As the broaching force increases, the bending rigidity also increases. When the force of the No. 40 blade is increased from 5kN spectrum to 15kN, the bending excitation T is increased from 11N / "m to 13N /" m ° 3. The pulling force will affect the dynamic characteristics of the joint point of the handle, that is, the greater the pulling force, The higher the natural frequency (natura frequency), but the damping ratio (damping ratio) will decrease. It has been found from many documents that increasing the broaching force has a positive effect of stabilizing the machinability of the handlebars. However, the greater the broaching force, the greater the force required to hold the knife. That is, it still has a negative effect. Studies in various literatures tend to influence the changes of the broaching force on the aforementioned characteristics of the main shaft * To help the rib designer determine the optimal broaching force, but for the literature that actually discusses the broaching force changes during rotation of the broaching mechanism Very _ 3-This paper scale is applicable to the Chinese National Standard (CNS) A4 specification (210X297 mm) (please read the precautions on the back before filling out this page) Packing-ΛMinistry of Economic Affairs ^ 0 Central Standards Bureau employee consumption cooperation 24 printing 5 Employee Consumer Cooperation System P7 Bureau of the Ministry of Economic Affairs Α7 Β7 V. Description of the invention (3) An invention that can suspend and measure spindle broaching force in static state has been seen in US Patent No. 4,856,349, which is used in the load sensor (Load When the shaft in the cell is displaced, the force generated on both sides of the load sensor is sensed by M, and the conversion is displayed as the broaching force. Another product is the shaft tension tester designed and produced by the German company UTILIS MUELLHEIM. It is characterized by modularization and digital display of measurement data. It also provides appropriate measurements for spindles with different tool handle specifications. Its shortcoming is that it only provides static broach force measurement. • The rotating spindle does not provide measurement capabilities. Whether the spindle rotation has an effect on the broach mechanism, or even the reduction of the broach force is all theirs. Neglected. The measurement of the broaching force is difficult when the measurement device is designed from the viewpoint of system design. The broaching mechanism itself is a rotating body, and its rotation speed can reach tens of thousands of revolutions per minute. * If a strain gauge is used gages) and the dynamometer to measure the broach force can only be applied to static measurement. However, during the dynamic measurement process, the measurement number will not be received externally, resulting in measurement failure. In order to achieve the purpose of dynamic measurement, in the process of the present invention, a device called slip rings was used to make the connecting parts of the rotating machine achieve the connection of the lead wire and use the brush to rotate The signal is transmitted to the same external contact. The concept has been discussed in depth, but based on the complexity of construction and use • From the consideration of manufacturing and maintenance costs, this method has been abandoned. The purpose of this case is to provide a non-contact method for measuring the broach force. 4-1 I -------------------- r # — (please read the back Note to fill out this page)
JJ
A 本紙張尺度適用中國國家標準（CNS ) Μ規格（210X297公釐） 318887 A7 B7 五、發明説明（4 ) 1 本案的次一目的，在提供一種可最測靜態或動態拉刀 力的方法。 本案的再一目的，在提供一種最測儀，可量測主軸靜 態或動態中的拉刀力。 5 本案的又一目的，在提供一種董測機構•將主軸的拉 刀力轉換成一位移量，供位移感測器董測並加Μ換算處理。 本案的進一目的，在提供一種量測機構，將利用彈性 元件規範量測機構內滑動袖的位移量。 本案係將被測試的主軸拉刀力，依董測機構中特別的 彈性元件的設定常數值，轉換成一位移量*該位移童供一 固定的位移感测器感測。位移感测器感测的位移乘以依彈 性元件所設定的常數值，修正後即可獲得主軸內拉刀機構 的實際拉刀力值。 經濟部2fo央標準局員工消費合作244印製 (請先閲讀背面之注意事項再填寫本頁) 量測機構的滑動軸受主袖拉刀力作用時，會產生一袖 向位移，一葺到該拉刀力與最測機構內的彈性元件產生的 阻力彼此平衡時才停止。位移感測器固定地裝設在最測機 構的滑動袖附近，Μ非接觸的方式董測位移童*再轉換成 拉刀力的值。因此*不管量测機構被受量测的主軸内的拉 刀機構所抓持（draw-in)後*主軸是在靜止或旋轉中皆可 進行量測。 量測機構並且可^有調整元件*調整彈性元件的阻力 ，Μ先行設定拉刀力值的量測下限值。彈性元件在旋轉中 受雛心力的影響*則由可調整設定的常數值對位移感測器 的童測值加以補償。 一 5 -A This paper scale is applicable to the Chinese National Standard (CNS) M specifications (210X297mm) 318887 A7 B7 V. Description of the invention (4) 1 The purpose of this case is to provide a method for measuring static or dynamic broaching force. Another purpose of this case is to provide a measuring instrument that can measure the broaching force of the spindle in static or dynamic state. 5 Another purpose of this case is to provide a Dong measuring mechanism to convert the broaching force of the spindle into a displacement amount for the displacement sensor to measure and add M conversion processing. A further object of this case is to provide a measuring mechanism that will use elastic elements to standardize the displacement of the sliding sleeve in the measuring mechanism. In this case, the spindle broaching force to be tested is converted into a displacement amount according to the set constant value of the special elastic element in the measuring mechanism *, and the displacement child is sensed by a fixed displacement sensor. The displacement sensed by the displacement sensor is multiplied by the constant value set by the elastic element, and the actual broaching force value of the broaching mechanism in the spindle can be obtained after correction. Printed by the Consumers ’Cooperation Cooperative 244 of the 2FO Central Standards Bureau of the Ministry of Economic Affairs (please read the precautions on the back before filling out this page) When the sliding shaft of the measuring mechanism is subjected to the force of the main sleeve broach, a sleeve-direction displacement will be generated. The broaching force and the resistance generated by the elastic element in the measuring mechanism are balanced when they stop each other. The displacement sensor is fixedly installed near the sliding sleeve of the most measured mechanism. The displacement is measured in a non-contact manner * and then converted into the value of the broaching force. Therefore * regardless of whether the measuring mechanism is drawn-in by the broaching mechanism in the spindle under test * the spindle can be measured while it is stationary or rotating. The measuring mechanism can also have an adjustment element * to adjust the resistance of the elastic element, M first set the lower limit of the measurement of the broach force value. The elastic element is influenced by the heart force during rotation *, and the adjustable constant value is used to compensate the child measurement value of the displacement sensor. 1 5-
張尺度適用中國國家標準（CNS ) Α4規格（21〇X297&H 318887 ΑΊ B7 5 五、發明説明（5 ) 兹配合Μ下附圖說明本案的較佳實施例，俾進一步了 解本案之特徵與功效。 圖式的簡單說明： 第1圖是本案量測機構較佳實施例的剖視圃。 第2圖是類似於第1圖》但顯示另一實施例。 第3圖是類似於第1圖，並且顯示量測機構的第三種實 施例。 第4Α圖與4Β圖分別顯示第1圖的最測機構裝設在工具 機刀軸上的情形，其中第4Β圖顯示刀軸内的拉刀 機構施加拉刀力於董測機構後的狀態。 第5圖是本案應用的螺旋弾賛靜態誤差表。 第6圈是本案應用的各種代表性弾簧在不同轉速中， 軸向位移之變化曲線表。 第7圖是主軸轉速與量测位移相對變化的曲線圖。 第8圖是主袖轉速與拉刀力相對變化的曲線圖。 本案提供的量測方法•是： (a) 先結合一支持物於工具機主軸的端部； (b) 樞設一具有一凸出部的滑動件在支持物的中央， 並使主軸內的拉刀機構夾持著該滑動件的一端； (c) 選擇並預先置放一彈性元件在支持物與滑動件凸 出部之間，以對滑動件被拉動時產生阻力； (d) 依彈性元件的特佳預設一常數； (e) 調整彈性元件的被歷縮力，以預先設定滑動件被 拉動的最小力量。 —6 — 本紙張尺度適用中國國家標準（CNS ) A4规格（210X297公釐） I _ ^ 装 I I I I I 訂 (請先閲讀背面之注意事項再填寫本頁) 經濟部g央標準局貝工消費合作說印製 A7 B7 五、發明説明（6 ) 1 (f) 固定一位移感測器並藉以感測滑動件的位移量； 與 (g) 取被選擇的彈性元件的常數，乘Μ感測所得之位 移量以獲得拉刀力值。 5 (請先閲讀背面之注意事項再填寫本頁) 其中位移感測係Μ非接觸量測的形態，對準於滑動件 端部側面而童測為一最佳模式。 用於量測尺寸的感測器，為非接觸式之位置感測器， 商品化之位置感測元件（PSD)非常多，如日本KEYENCE的 LC2320雷射位移計與LC2100控制器組合，是一已商品化 且可加以採用的裝置。 量測過程中，若誤差因素存在著卻不去發掘並克腋， 將導致量測结果的不準確。在誤差因素中影響最大的是彈 性元件。該强性元件可在螺旋形彈簧、多數曼合在一起的 盤形彈簧（Belleville springs)、有彈性的橡膠或塑膠管 、或其他等效元件中加Μ採用。 經濟央梂準局員工消費合4印袋 彈性元件的常數值依各彈性元件的材料、結構、加工 狀態等會有不同，但都可Μ預先參考第5或6圖獲知。目前 最方便取用的彈性件是螺旋狀壓力彈賛，其旋轉中軸向位 移的變形量ΔΥ可由下式求得： △ Y = L (Sin po — Sin pi) 其中L是彈簧螺線長度，Po是旋轉前之彈簧螺距角，？1是 旋轉後之螺距角的變化。 依前述方法實施的一具體設備，請參考第1圖所示， 包括一量測機構（2)，及一位移感測器（1)固定地裝設於量 —7 ~ 本纸張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） 1 5 10 15 經 2¾ 標 準 局 貝 工 消 合 作 4 製 IS δ α 7 Α7 Β7 五、發明説明（ 7 測機構（1)的滑動軸量測端的附近’ Μ偵測濟動軸的位移 值。 量測機構（2)係供套裝於主軸（3)的端部，被主軸内的 拉刀機構（31)夾持’其主要具有一中空的本體（21)，一滑 動軸（22)與一彈性元件（24)。本體（21)第一端的外緣為― 斜錐體（211)，俾套合於主軸（3)的錐孔。一滑動軸（22)則 滑動自如地裝設在本體（21)內，該滑動軸（22)有一量測端 (221)與一被夾持端（222)，個別地露出於本體（21)的兩側 端；滑動軸（22)的腰部有一滑動件（23)隨著滑動軸（22)移 動。彈性元件（24)在圖中係顯示應用一螺旋狀壓縮弾簧， 在本體（21)內保持於滑動件（23)與本體（21)的內部之間， 用來阻擋滑動件朝本體（21)的第一端移動。因此，被測的 拉刀力至少必須大於強性元件（24)的張力，才可拉動滑動 軸；滑動軸移動後一直移動到當拉刀力與彈性元件的張力 相等時才會停止。若藉著一調整元件（詳後述）調整滑動件 (23)與本體（21)間的相對位置，則可調整彈性元件（24)的 張力，而預設滑動軸（22)被拉動的最小力量。 在圖1的實施例中，調整元件（25) Μ螺紋鎖在本體（21 )上*且有一螺帽（251)協助鎖定位置。滑動件（23)滑動自 如地套在調整元件（25)內，但係以螺紋鎖在滑動軸（22)上 ，且亦有一_緊螺帽252使之定位。滑動件（23)藉螺紋可用 以調整滑動軸（22)與主軸（3)内拉刀機構（31)的距離，使拉 刀機構（31)可確實夾持住滑動軸（22)的被夾持端（222)，且 可使滑動件（23) _著滑動軸（22)—齊在本體（21)調整元件 -8 - (請先閱讀背面之注意事項再填寫本頁) 、-* 本紙張尺度適用中國國家榡準（CNS ) Α4規格（210X297公釐） ^ 〇 f- r\ vm j.〇〇d7 A7 B7 1 5 經濟部標準局貝工消費合作製 五、發明説明（8 ) (25)內滑動自如。 圖2的另一實施例，則利用一旋在滑動軸（22)上的螺 帽（26)做為調整元件兼做為滑動件，雖然也是應用螺紋來 調整其與本體（21)間的相對位置，但必須不斷地拆、裝本 體上的後蓋（27)，操作較為麻煩。 圖3的再一實施例，如同圖2之第一個實施例一樣，是 本體（21)的斜錐體部份係以組裝方式構成，此例另與圖1 的前述第一個實施例不同處，是將滑動件（23) M—滑環及 螺管共同組成。 彈性元件（24) Μ採用圖例中的螺旋形壓縮彈簧為較佳 ，雖然也可採用拉縮彈簧，但將無法對滑動件構成較理想 的阻力。無論如何，被測的拉刀力是等於彈性元件（24)的 阻力，就壓縮彈簧而言，阻力即是弾簧抵抗被腰縮的力量 。拉刀力（F)可由下式表示： F = Κ . △ <5 其中Κ是依彈性元件修正的常數，AS則是滑動軸（22)的 位移，該位移如前所述是由位移感測器（1)測得，該位移 感測器（1)上若設有一數值顯示器（U)將更便於立即讀取 拉刀力數值。 本體（21)的第一端最好是M7:24的斜度構成斜錐體 (211)，以便與廣泛的工具機的主軸孔配合。量測機構（2) 套裝在主軸（3)後的量測狀態，由第4A與4B圖分別顯示Μ 壓縮彈簧作為彈性元件為例，其在旋轉中對量測位移的 影響性。 -9 - 本紙張尺度適用中國國家標準（CNS ) A4規格（210X297公着） (請先閱讀背面之注意事項再填寫本莧) ir φ. 〇± 8〇d7 A7 B7 五、發明説明（g ) 1 5 (請先閲讀背面之注意事項再填寫本頁) 第5圖顯示螺旋彈簧靜態誤差，其中理論值K1可由彈 簧供應商獲得，實驗值K2則係經發明人Μ材料試驗機實驗 測得的數值，是一直線性的形態，其斜率與修正後的實際 曲線Κ3是一樣的，由此圖可由被感測的位移量，直接讀出 本案量測方法所知的拉刀力（Ν)。本案的量測機構在動態 試驗中，可獲得第7圖的量測值（measure curve)，但本案 在發現如第6圖等潛在的影響因素後，提供一誤差值（error curve)以供修正量測值可獲得一較正確的曲線值（exact curve)。由於第7圖量測位移在旋轉中的變化，相對地顯 示第8圖的结果即拉刀力亦會同時變化*此第7與8圖是本 案實施例實驗後的结果，而此等當主軸在旋轉中產生的潛 在因素在此之前並未被發覺。 圖5中修正後實際值曲線乃由圖中實驗值曲線原點偏 移而來，其修正後實際值曲線斜率值K3亦相等於實驗值曲 線之斜率K2，然兩者彈簧受力於彈簧J1S縮量之關係並不相 同。此乃因吾人由材料試驗機所得實驗值，僅可由其斜率 變化得知彈簧之彈黄常數K2，因此依據虎克定律F=K2.X， 可得修正後實際值曲線。 經濟部2ΙΌ央標準局員工消費合作24印製 本發明中可使用不同彈簧來增加所量測拉刀力之範圍 ，圖6中TB、ΤΗ、TM、TL即分另[I代;表不同規格之彈簧，W,t 貝ii代表該形式彈簧其螺線（spring wi re)截面（cross section)之尺寸0 匾17中，量測曲線為本發明之量測儀在實際之工具機 蓮轉之主軸上所量測之位移變形量’而在動態量測過程因 —10 一 本紙張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） 5 Α7 Β7 五、發明説明（10 ) 有潛在的誤差因素即誤差曲線之存在，故需合成此兩曲線 从得至ΓΗ參正曲線，Jtb修正曲線即為真實之旋轉主軸拉刀力 變化所導致量測儀上位移之變化。而誤差曲線乃經由圖6 所得。 在圖7中，修正曲線為真實之旋轉主軸拉刀力變化所 導致量測儀上位移之變化，因此根據本設計之原理，此修 正曲線即為主軸拉刀力變化導致量測儀之彈簧產生位移變 化，故此位移變化乘以彈簧修正後之彈簧常數K3，即為圖 8中，拉刀力變化之曲線。此一结果可得知主軸不同轉速 下拉刀力變化情形，達到本設計發明動態量測之目的。 本案提供了一個特別的方法與機構，使主軸的拉刀力 的测試更成熟與方便，並突破了往昔無法在主軸旋轉中量 測的瓶頸。 在上述圖示中，雖然舉出一些ί較佳之實施例以陳明本 案之可行性，但如眾所知，不宜由該實施例反而限制了本 案下述之申請專利範園，亦即，任何熟悉此藝者若應用本 案主要之特徵，進行若干细節的變化，皆仍應靥於本荼之 專利範圍所含括者。 (請先閱讀背面之注意事項再填寫本頁) 訂 -1- ! 經濟部20央標準局貝工消費合作^印製 -11 - 本紙張尺度適用中國國家梯準（CNS ) Α4規格（210X 297公釐）The Zhang scale applies the Chinese National Standard (CNS) Α4 specification (21〇X297 & H 318887 ΑΊ B7 5 V. Description of the invention (5) The following is a description of the preferred embodiment of this case in conjunction with the following drawings, so as to further understand the characteristics and efficacy of this case Brief description of the drawings: Figure 1 is a cross-sectional view of the preferred embodiment of the measuring mechanism of the case. Figure 2 is similar to Figure 1 but shows another embodiment. Figure 3 is similar to Figure 1 And shows the third embodiment of the measuring mechanism. Figures 4A and 4B show the installation of the most measuring mechanism of Figure 1 on the tool shaft of the machine tool, where Figure 4B shows the broach in the tool shaft The state of the mechanism after applying the broaching force to the Dong measuring mechanism. Figure 5 is the static error table of the spiral pressure applied in this case. Circle 6 is the variation curve of the axial displacement of various representative springs applied in this case at different speeds Table 7. Figure 7 is a graph of the relative change of the spindle speed and the measured displacement. Figure 8 is a graph of the relative change of the main sleeve speed and the broach force. The measurement method provided in this case is: (a) First, combine one The support is at the end of the machine tool spindle; (b) Set a sliding member with a protruding part in the center of the support, and make the broaching mechanism in the main shaft hold one end of the sliding member; (c) Select and place an elastic element in advance on the support and the sliding member Between the protruding parts, to generate resistance when the slider is pulled; (d) According to the best preset of a constant of the elastic element; (e) Adjust the contraction force of the elastic element to pre-set the slider to be pulled Minimum strength. —6 — This paper scale is applicable to the Chinese National Standard (CNS) A4 specification (210X297mm) I _ ^ Packed with IIIII (please read the precautions on the back before filling this page) Ministry of Economics g Central Standards Bureau Bei Gong Consumer cooperation theory printed A7 B7 V. Description of invention (6) 1 (f) Fix a displacement sensor and use it to sense the displacement of the sliding member; and (g) Take the constant of the selected elastic element, multiply the Sense Measure the displacement to obtain the broach force value. 5 (Please read the precautions on the back before filling in this page) where displacement sensing is the form of non-contact measurement, which is aligned with the side of the end of the slider and measured It is the best mode. The sensor used to measure the size , Is a non-contact position sensor, there are many commercial position sensing elements (PSD), such as Japan KEYENCE LC2320 laser displacement meter and LC2100 controller combination, is a commercialized and can be used device In the measurement process, if there is an error factor but not to excavate and overcome the axillary, it will lead to inaccurate measurement results. Among the error factors, the most important thing is the elastic element. This strong element can be used in helical springs, most Belleville springs, elastic rubber or plastic tubes, or other equivalent components are used in the combination of M. The constant value of the elastic elements of the 4th printed bag of the Economic and Industrial Security Bureau staff depends on each elasticity. The material, structure, processing status, etc. of the element will be different, but all can be obtained by referring to Figure 5 or 6 in advance. At present, the most convenient elastic part is the spiral pressure spring. The amount of deformation of the axial displacement during rotation can be obtained by the following formula: △ Y = L (Sin po — Sin pi) where L is the length of the spring spiral, Po is the spring pitch angle before rotation ,? 1 is the change in pitch angle after rotation. For a specific device implemented according to the aforementioned method, please refer to Figure 1 and include a measurement mechanism (2) and a displacement sensor (1) fixedly installed in the measurement-7 ~ This paper size is applicable to China National Standard (CNS) A4 specification (210X297 mm) 1 5 10 15 After 2¾ standard Bureau of the Ponggong Consumer Industry Co., Ltd. 4 system IS δ α 7 Α7 Β7 V. Description of the invention (7 Near the sliding shaft measuring end of the measuring mechanism (1) 'M detects the displacement value of the actuating shaft. The measuring mechanism (2) is provided for the end of the main shaft (3), and is clamped by the broaching mechanism (31) in the main shaft. It mainly has a hollow body ( 21), a sliding shaft (22) and an elastic element (24). The outer edge of the first end of the body (21) is an oblique cone (211), which fits into the tapered hole of the main shaft (3). One slide The shaft (22) is slidably installed in the body (21). The sliding shaft (22) has a measuring end (221) and a clamped end (222), which are individually exposed to the two sides of the body (21) Side end; a sliding member (23) moves along the sliding shaft (22) at the waist of the sliding shaft (22). The elastic element (24) is shown in the figure to apply a helical compression The spring, held in the body (21) between the slider (23) and the interior of the body (21), is used to block the slider from moving toward the first end of the body (21). Therefore, the measured broach force is at least It must be greater than the tension of the strong element (24) to pull the sliding shaft; after the sliding shaft moves, it will stop until the broaching force is equal to the tension of the elastic element. If it is adjusted by an adjusting element (described later) The relative position between the sliding member (23) and the body (21) can adjust the tension of the elastic element (24), and preset the minimum force that the sliding shaft (22) is pulled. In the embodiment of FIG. 1, the adjusting element (25) M thread is locked on the body (21) * and a nut (251) assists the locking position. The sliding member (23) slides freely in the adjusting element (25), but is locked with a thread on the sliding shaft ( 22), and also has a tightening nut 252 to position it. The sliding member (23) can be used to adjust the distance between the sliding shaft (22) and the main shaft (3) broach mechanism (31) through the thread, so that the broach mechanism (31) can surely hold the clamped end (222) of the sliding shaft (22), and can make the sliding member (23) _ Slide shaft (22) —aligned with the body (21) to adjust the components -8-(please read the precautions on the back before filling in this page),-* The paper size is applicable to China National Standard (CNS) Α4 specification (210X297mm ) ^ 〇f- r \ vm j.〇〇d7 A7 B7 1 5 Ministry of Economic Affairs Bureau of Standards Beigong Consumer Cooperation System V. Description of invention (8) (25) Sliding freely inside. Another embodiment of FIG. 2, use A nut (26) screwed on the sliding shaft (22) serves as an adjusting element and also serves as a sliding member. Although the thread is used to adjust its relative position with the body (21), the body must be disassembled and assembled continuously The upper back cover (27) is troublesome to operate. Another embodiment of FIG. 3, like the first embodiment of FIG. 2, is that the oblique cone portion of the body (21) is constructed in an assembled manner, and this example is different from the aforementioned first embodiment of FIG. At the place, it is composed of the sliding part (23) M-slip ring and the solenoid. The elastic element (24) M is preferably a spiral compression spring as shown in the figure. Although a tension spring can also be used, it will not be able to form an ideal resistance to the sliding member. In any case, the measured broach force is equal to the resistance of the elastic element (24). In terms of compression springs, the resistance is the force of the spring against the waist contraction. The broaching force (F) can be expressed by the following formula: F = Κ. △ < 5 where K is a constant corrected by the elastic element, AS is the displacement of the sliding shaft (22), and the displacement is determined by the displacement Measured by the sensor (1), if a numerical display (U) is provided on the displacement sensor (1), it will be more convenient to immediately read the value of the broaching force. The first end of the body (21) preferably has a slope of M7: 24 to form a tapered cone (211), so as to fit with the spindle hole of a wide range of machine tools. The measurement state after the measurement mechanism (2) is fitted on the main shaft (3). Figures 4A and 4B show the M compression spring as an elastic element as an example, and its influence on the measurement displacement during rotation. -9-This paper scale is applicable to the Chinese National Standard (CNS) A4 specification (210X297 public) (please read the precautions on the back before filling in this amaranth) ir φ. 〇 ± 8〇d7 A7 B7 V. Description of the invention (g) 1 5 (Please read the precautions on the back before filling this page) Figure 5 shows the static error of the coil spring. The theoretical value K1 can be obtained by the spring supplier, and the experimental value K2 is measured by the inventor M material testing machine. The value is always linear, and its slope is the same as the actual curve K3 after correction. From this figure, the broaching force (Ν) known in the measurement method can be directly read from the displacement sensed. The measurement mechanism of this case can obtain the measurement value of Figure 7 in the dynamic test, but after finding the potential influencing factors such as Figure 6 in this case, an error curve is provided for correction The measured value can obtain a more accurate curve value (exact curve). As Figure 7 measures the change in displacement during rotation, the result of Figure 8 is relatively displayed, that is, the broaching force will also change at the same time. * Figures 7 and 8 are the results after the experiment of the example of this case, and this is equivalent to the main shaft. The potential factors generated in the rotation have not been noticed before. The corrected actual value curve in Figure 5 is derived from the origin of the experimental value curve in the figure. The slope K3 of the actual value curve after correction is also equal to the slope K2 of the experimental value curve, but the springs of both are subjected to spring J1S The relationship of shrinkage is not the same. This is because we obtained the experimental value from the material testing machine, and we can only know the spring yellow constant K2 of the spring from its slope change. Therefore, according to Hooke's law F = K2.X, we can get the corrected actual value curve. Employee consumption cooperation of the Ministry of Economic Affairs 2ΙΥCentral Standards Bureau 24 Printing In this invention, different springs can be used to increase the range of measured broach force. The spring, W, t and ii represent the size of the spring wi re cross section of this type of spring. In the plaque 17, the measurement curve is the measurement tool of the invention in the actual machine tool. The amount of displacement and deformation measured on the spindle's dynamic measurement process because of -10 a paper scale applicable to the Chinese National Standard (CNS) A4 specifications (210X297 mm) 5 Α7 Β7 5. Invention description (10) Potential The error factor is the existence of an error curve, so it is necessary to synthesize these two curves from the ΓΗ reference positive curve. The Jtb correction curve is the change in the displacement of the measuring instrument caused by the change of the real rotating spindle broaching force. The error curve is obtained through Figure 6. In Fig. 7, the correction curve is the change of displacement on the measuring instrument caused by the change of the actual rotating spindle broaching force. Therefore, according to the principle of this design, this correction curve is the change of the spindle broaching force resulting in the spring of the measuring instrument. The displacement changes, so the displacement change is multiplied by the spring constant K3 after the spring correction, which is the curve of the broach force change in Figure 8. This result shows the change of the pull-down force of the spindle at different speeds, which achieves the purpose of dynamic measurement of the present design. This case provides a special method and mechanism to make the testing of the broaching force of the spindle more mature and convenient, and breaks through the bottleneck that could not be measured during the rotation of the spindle. In the above illustration, although some preferred embodiments are cited to illustrate the feasibility of this case, as is known, it is not appropriate for this embodiment to limit the scope of the patent application for the following cases in this case, that is, any Those who are familiar with this artist should apply the main features of this case and make some changes in details, which should still be included in the scope of this patent. (Please read the precautions on the back before filling out this page) Order -1-! 20 Central Standards Bureau of the Ministry of Economic Affairs Beigong Consumer Cooperation ^ Printed-11-This paper size is applicable to China National Standards (CNS) Α4 specifications (210X 297 Mm)