200823005 - y 九、發明說明： 【發明所屬之技術領域】 本發明係有關於一種加工機機構，更詳而言之，係有 關於一種車銑複合加工機B軸驅動機構。 【先前技術】 機械加工是製造工業上的基本需求，舉凡平面精度、 工件肉厚精度等所需之加工製造考量皆須使用各式加工 工具機來協助完成’然而加工工具機發展快速且技術不斷 進v例如車床的加工機已由傳統的傳統式普通車床、 CNC(電腦數值控制）車床發展到多軸化、高速化、及高精 度化的車銑複合化型式，在這些改良進步下加工工具機的 S又计優劣則會直接導致加工產品的精度問題以及加工機 的壽命問題，例如機械加工方面，在銑削、車削等加工法 上，加工機的機件組合若是設計不當則容易有扭矩不足、 傳動齒为隙在長時間使用後需調整、或不適合做連續加工 等問題發生，若使用後還需數次調整才可恢復原有加工精 度則亦造成極大的不便。 如歐洲專利EP0899057號所揭示的驅動機構，請參閱 第1圖，即採用伺服馬達11以正齒輪12將動力傳遞於銑 削主轴13，而此種傳遞動力之方式係與銑削主軸13所組 合的B軸模組14以間接驅動系統來產生迴轉運動，致使 銳削主軸13可根據b軸模組14的驅動而產生預定分度角 度之擺動’但由於正齒輪12傳動速比較小無法提供大扭 矩輸出’所以比較不適於做連續加工的應用，且正齒輪 5 19856 200823005 12在安裝時不易調整，加工後再調整精度也不容易，因 此產生傳動齒背隙不易消除等缺點，實不適合作為B轴的 驅動機構。 ' ' 有鑑於習知技術無法提供大扭矩輸出之問題，日本專 利JP2001322001案提出克服技術，請參閱第2圖，該 術係採用祠服馬達（未圖示）經蜗桿21將動力傳遞於銳 削主軸（未圖示），而此種傳遞動力之方式係與銳削主軸 所組合的B軸模故經從動件竭輪2 2以間接驅動系統來產 生迴轉運動，相對於使用齒輪的驅動機構，以蜗輪 =有較大的減速能力以及較大的扭矩放大仙，但以蜗 輪22產生之傳動則因齒距較大不適合高速化之傳動，且 虫尚輪2 2傳動之背隙雷f么τ' 項m敕 在長時間使用過後必 須再進仃调正以保持較佳之傳動精度，是故非常不便。 為解決習知技術之傳動齒背隙以及無法具有大扭矩 輸出等問題，如第3 pi % 一 中，遂提出專利EP1647355A1案 減、#做“二 馬達31先將動力傳遞於正齒輪32 減速做扭矩放大，再將動力依序傳遞至凸輪％ 351，使其透過滾子351盥 /c 〇4 ^ ^ ”凸輪州之彳合配帶動β軸模組 用 是較為複雜的間接馬區動系統，由於該 可提τ供傳33輪廊與滾子351之間的滾動摩擦，故 二導致:動力’但由於凸輪3 3的轉角加工不易 損，而ftt件35的滾子351與&輪33之間易於磨 二 k成傳動比不一的狀況，因此無法逵到曰丨Μ、隹仏 單位，除此之外，&於q q 取小々進、， 凸輪33的輪廓製作較為複雜，如何達 19856 6 200823005 到所需之加工精度，仍為需要克服之關鍵技術。 因此，有效解決前揭枯外 有直接驅動能力之驅動機構:將首：之問題，開發出-具 ^ ^ 钺構將直接驅動的效果直接傳到 避㈣過傳動變逮機構以提高定位精度及加工精 度，貫為目丽所亟待解決之課題。 【發明内容】 ，以上所述先前技術之缺點，本發明之主要目的即 =提供-種車銳複合加工機β軸驅動機構，俾提升定位 褙度及加工精度。 本發明之次要目的在於提供一種車銳複合加工機β 轴驅動機構’俾利於連續加工作業，提高加工效率。 為=揭目的以及其他目的’本發明提供一種車銳複 R° &轴驅動機構’係應用於驅動車銳複合加工機之 人車^疋轉動件’至少包括··滑座，係滑動設置於該車銳複 ;口工於上，並供轉動配置該Β軸旋轉動件；直接驅動馬 ^係至少具有固定於該滑座之馬達定子、及藉由該馬達 疋子激磁而驅轉之馬達轉子，且該馬達轉子並固定至辞β 軸旋轉動件’·以及離合齒模組，係配置於該滑座盘該: 軸旋轉動件之間，以供選擇性地切換該Β軸旋轉動件” 滑座之定位狀態。 人 前述本發明之加工機Β軸旋轉機構車銑複合加工 軸驅動機構中，該離合齒模組係可包括固定至該Β轴旋 動件之離合齒旋轉動件、岐至該滑座之離合齒固定件Τ 以及可切換位置而選擇性地同時嗜合該離合齒旋轉動件 19856 7 200823005200823005 - y IX. DESCRIPTION OF THE INVENTION: TECHNICAL FIELD The present invention relates to a processing machine mechanism, and more particularly to a B-axis driving mechanism for a turning and milling machine. [Prior Art] Machining is a basic requirement in the manufacturing industry. The processing and manufacturing considerations required for plane accuracy, workpiece thickness accuracy, etc. must be assisted by various machining tools. However, the development of machine tools is fast and technologically advanced. The processing machines such as lathes have been developed from traditional conventional lathes and CNC (computer numerical control) lathes to multi-axis, high-speed, and high-precision turning and milling composite types. The advantages and disadvantages of the machine S will directly lead to the accuracy of the processed products and the life of the processing machine. For example, in machining, in the machining methods such as milling and turning, if the machine parts of the machine are not properly designed, it is easy to have insufficient torque. The transmission tooth is a problem that the gap needs to be adjusted after long-term use, or is not suitable for continuous processing. If it is adjusted several times after use, the original machining accuracy can be restored, which also causes great inconvenience. For example, in the driving mechanism disclosed in European Patent No. EP0899057, referring to Fig. 1, the servo motor 11 is used to transmit power to the milling spindle 13 with the spur gear 12, and the manner of transmitting the power is combined with the milling spindle 13 The shaft module 14 generates a rotary motion by an indirect drive system, so that the sharpening spindle 13 can generate a swing of a predetermined indexing angle according to the driving of the b-axis module 14 but the large-torque output cannot be provided due to the relatively small transmission speed of the spur gear 12 'So it is not suitable for continuous machining applications, and the spur gear 5 19856 200823005 12 is not easy to adjust during installation. It is not easy to adjust the precision after machining. Therefore, it is not easy to eliminate the backlash of the gear teeth. It is not suitable as a B-axis. Drive mechanism. ' 'In view of the fact that the conventional technology cannot provide the problem of large torque output, the Japanese patent JP2001322001 proposes to overcome the technique. Please refer to Fig. 2, which uses a squirrel motor (not shown) to transmit power to the worm through the worm 21 The spindle is cut (not shown), and the way of transmitting the power is the B-axis module combined with the sharpened spindle. The indirect drive system is used to drive the rotary motion through the follower wheel 2 2, relative to the drive using the gear. The mechanism, with the worm wheel = has a large deceleration capacity and a large torque amplification, but the transmission generated by the worm wheel 22 is not suitable for high-speed transmission due to the large pitch, and the backlash of the insect wheel 2 2 transmission The τ' item m敕 must be adjusted again after long-term use to maintain better transmission accuracy, which is very inconvenient. In order to solve the problem of the transmission backlash of the prior art and the inability to have a large torque output, such as the 3rd pi % one, the patent EP1647355A1 is reduced, and the #2 motor 31 first transmits the power to the spur gear 32 to decelerate. The torque is amplified, and then the power is transmitted to the cam % 351 in sequence, so that it passes through the roller 351 盥 / c 〇 4 ^ ^ ” The combination of the cam state and the β-axis module is a complicated indirect horse-moving system. Since the τ can transmit the rolling friction between the 33 rim and the roller 351, the second result is: power 'but because the corner processing of the cam 3 3 is not easily damaged, and the roller 351 and the & wheel 33 of the ftt member 35 It is easy to grind two k into different transmission ratios, so it is impossible to get 曰丨Μ, 隹仏 units, in addition, & in qq take small 々,, the contour of the cam 33 is more complicated, how to Up to 19856 6 200823005 to the required processing accuracy, still the key technology to be overcome. Therefore, it is effective to solve the drive mechanism that has direct drive capability before the release: the first problem: the development of the ^ ^ structure will directly drive the effect directly to avoid (four) over the transmission change mechanism to improve the positioning accuracy and Machining accuracy is a problem that needs to be solved. SUMMARY OF THE INVENTION In view of the above-mentioned shortcomings of the prior art, the main object of the present invention is to provide a β-axis drive mechanism for a car-sharp composite machining machine, which improves the positioning twist and the machining accuracy. A secondary object of the present invention is to provide a β-axis drive mechanism for a vehicle-sharp composite machine, which facilitates continuous machining operations and improves machining efficiency. For the purpose of deliberation and other purposes, the present invention provides a vehicle sharp R° & shaft drive mechanism for use in a vehicle for driving a vehicle with a sharp composite machine, which includes at least a sliding seat and a sliding setting. The vehicle is sharply resurfacing; the upper part of the machine is mounted thereon, and the rotating shaft member is configured to be rotated; the direct drive unit has at least a motor stator fixed to the sliding seat, and is driven by the motor tweezers to be driven by the motor. a motor rotor, and the motor rotor is fixed to the β-axis rotating member '· and the clutch tooth module, and is disposed between the shaft rotating member for selectively switching the shaft rotation The moving member "positioning state of the sliding seat. In the above-mentioned processing machine, the rotating shaft mechanism of the turning axis of the processing machine, the clutching gear module may include a clutch tooth fixed to the pivoting member of the pivoting shaft. a clutch member, a clutch tooth holder Τ to the slider, and a switchable position to selectively simultaneously engage the clutch tooth rotary member 19856 7 200823005
I ，件之離合齒套合動件。較佳地，該離合齒旋 動件PIU 4合㈣定件係可相鄰配置，而該離合齒套合 」立於該離合齒旋轉動件及離合齒固定件之上方可 動以切換位置。此外，該離合齒套合動件係可透過 油壓迴路驅動上下運動以切換位置。 緣之驅動機構復可包括設於該㈣旋轉動件之外 、古二…骨座之間的輛承’特別係一高精度轴承，其中，該 二係f:軸旋轉動件共軸，並設置於該B軸旋： 、、卩供支禮β軸旋轉動件，較佳地，該高精度 _度…直度接二達 提升為更具精度之傳動力馬達直接傳遞之動力， b轴4外機:發:狀…β轴旋轉機構車銑複合加工機 弓區動馬索 可包括固定於該滑座上以回授提昇直接 宜你ΐί驅動精度之編碼器，特別係一高精度編碼器， /、’、t、直接驅動馬達傳動精度之提升。 该B軸旋轉動件之轴心位置係包括_ β =其外部則可設有同該滑座上之化油路外1’ 衣’用以提供冷卻及潤滑油路。 由於本發明所提出之車銑複合加工機以驅 ί摆^係包括滑座、設於滑座上之直接驅動馬達、以及 軸旋轉動件與該滑座之定位狀態的離 口回輪、、且，俾達成車銑定角度加工時之+ 體剛性’復利用離合齒模組之離合齒套合動件向:脫:二 19856 8 200823005 合齒旋轉動件達成銑削持續擺動加工時 及加工：产且：匕將：用直接驅動之動力源提升定位精度 ΐ if H㈣”可完成所有工序，減少 所存在之問i 亚^加工效率，解決先前技術 【實施方式】 以下紋配合圖式說明本創作之且每 技術中具有通當知螞去_^-旦& Α八體只把例’以使所屬 與達成功I 輕易地瞭解本創作之技術特徵 機構=閱！ 4圖，係為本發明車銑複合加工機Β軸驅動 構5，。係庫不用思圖，如圖所示車銳複合加工機之6軸驅動機 :係應用於驅動車銑複合加工機之Β轴旋轉動件53, 主要係於一供轉動配置該Β軸旋轉動件Μ之滑座… ==馬達52與離合齒模組54，該直接驅動馬達二 則#供^ 該Β軸旋轉動件53，而該離合齒模組54 貝J係i、^擇性地切換該Β轴旋轉動件53與該滑座4之定 由於採用直接驅動設計，故具備高動態精度及零 、月隙等優點，而無機械效應上的損失，並利於連續加 工之應用。 、 μ配合翏閱第4圖及第5圖，本發明所指B軸驅動機 才5係應用於車銑複合加工機中’所屬技術領域中具有通 常知識者應均可了解所謂之_係泛指前述之滑座4、β 轴驅動機構5、以及B軸旋轉動件53等所構成之整體， 用以承載車銳複合加工機之銳削主軸6卜並藉由適當角 19856 9I, the clutch clutch sleeve of the piece. Preferably, the clutch-toothed rotary member PIU 4 is configured to be adjacently disposed, and the clutch-toothed sleeve is movably disposed above the clutch-toothed rotating member and the clutch-toothing member to switch positions. In addition, the clutch sleeve mover is driven to move up and down through the hydraulic circuit to switch position. The drive mechanism of the edge may include a bearing disposed between the (four) rotating member and the second member of the bone seat, in particular, a high-precision bearing, wherein the second system f: the shaft rotating member is coaxial, and Provided in the B-axis rotation: 、, 支 for the β-axis rotation of the moving member, preferably, the high-precision _ degree... straightness is increased to a more precise transmission power directly transmitted by the motor, b-axis 4External machine: hair: shape... β-axis rotating mechanism Turning and milling machine processing machine bow area moving horse can be fixed on the sliding seat to feedback the encoder that directly promotes your driving precision, especially a high-precision coding , /, ', t, direct drive motor drive accuracy. The pivot position of the B-axis rotating member includes _β = the outside of which can be provided with the defensive outer 1' garment on the sliding seat for providing cooling and lubricating oil passage. The turning and milling machine according to the present invention includes a sliding seat, a direct driving motor provided on the sliding seat, and an off-return wheel of the shaft rotating member and the positioning state of the sliding seat, Moreover, 俾 achieves the + body rigidity of the milling and milling angle processing. The clutch clutch gears of the reciprocating clutch module are: De: 219856 8 200823005 When the rotating gear of the tooth reaches the milling continuous machining process and processing: Production: 匕 :: Use the direct drive power source to improve the positioning accuracy ΐ if H (4) can complete all the processes, reduce the existing processing efficiency, solve the previous technology [implementation] The following pattern with the diagram illustrates the creation In each technology, there is a general knowledge of the _^- dan & Α 体 只 只 以 以 以 以 以 以 以 以 以 以 以 以 以 以 以 以 以 以 轻易 轻易 4 4 4 4 4 4 4 4 4 4 4 4 The turning and milling machine has a boring shaft drive mechanism 5. The system does not need to think about it. As shown in the figure, the 6-axis drive machine of the car-sharp composite machine is used to drive the slewing rotary member 53 of the turning and milling machine. Mainly in a rotation configuration Slider of the movable member... == motor 52 and clutch gear module 54, the direct drive motor 2 is for the shaft rotation member 53, and the clutch gear module 54 is J-type, selective Because the direct drive design is adopted, the spindle rotation member 53 and the slider 4 have the advantages of high dynamic precision, zero and monthly gap, and no mechanical effect loss, and are advantageous for continuous processing applications. With the cooperation of Fig. 4 and Fig. 5, the B-axis drive machine of the present invention is applied to the turning and milling machine for the B-axis drive machine. Refers to the above-mentioned slide 4, the β-axis drive mechanism 5, and the B-axis rotary member 53 and the like as a whole, for carrying the sharp-cut spindle 6 of the vehicle-sharp compounding machine and by the appropriate angle 19856 9
I 200823005 t * $ =的轉動提供相對於該銑削以61的分度仙， 利用該銑削主軸61進行連續加工作業之中 = 銳削主軸61相對於工件夾持模組62之角度變化貝進㈣ :轴：：機構5驅動車銑複合加工機之"由旋轉動件 53，至 > 由包括滑座4、直接 54，其中： ™与達52、及離合齒模組 該滑座4係滑動設置於該車銳複合加工機上，並 動配置该B軸旋轉動件53，以藉該B軸旋轉動件53 銑削主軸;以及離合齒模組，係配置於㈣座㈣β 2旋轉動件之間，以供選擇性地切換㈣軸旋轉 滑座之定位狀態。 一% 吞玄直接驅動馬達5 2将5 Φ目士^ π a … 有固定於該滑座之馬達 疋子523、及猎由該馬達定子如激磁而驅轉之馬達轉子 52卜藉由該馬達轉子521與馬達定子523的線圈之激磁 作用後驅動該馬達轉子521產生旋轉，其中，且該 子521並固定至該b軸旋轉動件％。 苛 該離合齒模組54係具有固定至Μ轴旋轉動件Μ 之離合齒旋轉動件543、固定至該滑座4之離合齒固定件 54卜以及可切触置而選擇性地同㈣合簡合齒 動件543及離合齒固定件541之離合齒套合動件545。於 本實施例中，該離合齒旋轉動件⑷及該離合齒固定件、 ⑷係相鄰配置’而該離合齒套合動件545難於該離合 齒旋轉動件543及離合齒固定件541之上方可上下運動以 切換位置。此外，該離合齒套合動件⑽係可透過一油屢 19856 10 200823005 i · * 迴路55驅動上下運動以切換位置。 且為供應銑削主軸61所需的冷卻及潤滑，該B軸旋 轉動件53之軸心位置包括一 B轴油路内環53卜其外部 則設有同軸固定於該滑座4上之β軸油路外環Η，用以 提供冷卻及潤滑油路。於本實_中，係湘油壓迴路 55所提供之油壓控制離合齒模組54之離合齒套合動件 545的作動，以使欲進行例如車削或銑肖仏王時，控制、、由 壓使該離合齒套合動# 545向下嗔合該離合齒固定件⑷ 及該離合齒旋轉動件543,由於該離合齒固定件Μ係血 該滑座4相固定，且該離合歯旋轉動件⑷係與μ㈣ 轉動件53相固定，故使離合齒套合動件545向下嗜合時 將該Β軸旋轉動件53與該滑座4相對固定，故可即時且 精確地鎖住切削主軸61之擺動功能，實現定角度加之需 求，並可提昇整體剛性及所需精度。 而 反之，利用油壓控制離合齒模組54之離合齒套合動 件545的作動，以於車削或銑削加工之間進行擺動分度調 整時，控制油璧使離合齒套合動件545向上脫離離合會固 定件541及離合齒旋轉動件543,以使該離合齒套合動件 545向上脫離該離合齒固定件541及離合齒旋轉動件5託 之％(合，亚控制直接驅動馬達52激磁驅動該^軸旋轉動 件53旋轉，開啟切削主轴61之擺動分度功能，實現連續 加工作業之往復擺動切換需求，其中由於採用直接驅動馬 達52構成之Β軸驅動機構5設計，故可避免習知技術中 傳動齒背隙之問題及高扭矩傳輸不足之問題，以具有高伺 19856 11 200823005 1 Λ 服響應極高動態精度之優勢。 ^是故，藉由本發明所組成之車銑複合加工機Β軸驅動 機構’可利用直接驅動馬達使負載的運動系統直接由馬達 的轉子驅動，動力傳遞中間無須任何減速機構或傳遞機構 用以間接傳動，故不會產生機械效益上的損失及傳動機構 間精度的誤差，除此之外亦具有無傳動背隙及高伺服響應 之優點。 θ 相較於習知技術，本發明所提出之車銑複合加工機f 軸驅動機構，湘離合齒模組以控制車銑複合銑削加工能 力’以離合齒模組之離合齒套合動件向下嚙合離合齿固^ 件、及離合齒旋轉動件遂達成車銑定角度加工時之 求並提升整體剛性；復利用離合齒模組之離合#套:= =脫;定件、及離合齒旋轉動件達成銑削持續 擺動加工時之精度需求，如此將利用 升定位精度及加工且使n挾㈣1112提 :::古減少ί成轉換所耗費之時間’並提高加工效率， 子已克服先前技術所存在之問題。 上述實施例僅例示性言兒明本發明之原理及 非用於限制本發明。任何所屬技術領域中罝 、而 均可在不違背本發明之精神及料下2 ^知識者 改變。因此，本發明之權利保護範圍行 申請專利範圍所列。 馮如後述之 19856 12 200823005 【圖式簡單說明】 第1圖係為習知B軸旋轉模組利 面示意圖； 回輪驅動結構剖 第f圖係為習知β軸旋轉模組利用蜗輪蜗桿 剖面示意圖； 焉區 動結構 第3圖係為習知β軸旋轉模組利用滾 f力驅動結構 側面示意圖； 驅動機構剖面 第4圖係為本發明車銑複合加工機β輛 示意圖；以及 弟5圖係為本發明應用有車銑複合加工機β 驅動機 構的車銑複合銳削加工機示意圖。 【主要元件符號說明】 11 伺服馬達 12 正齒輪 13 銳削主轴 14 Β轴模組 21 蜗桿 22 蜗輪 31 祠服馬達 32 正齒輪 33 凸輪 34 Β轴模組 35 從動件 351 滾子 19856 13 200823005 * - » 4 滑座 5 B軸驅動機構 52 直接驅動馬達 521 馬達轉子 523 馬達定子 53 B轴旋轉動件 531 B軸油路内環 54 離合齒模組 541 離合齒固定件 543 離合齒旋轉動件 545 離合齒套合動件 547 油壓迴路 55 B轴油路外環 6 床台 61 銑削主軸 62 工件夾持模組I 200823005 t * The rotation of $ = provides a division of 61 with respect to the milling, and the continuous machining operation is performed by the milling spindle 61 = the angle of the sharpening spindle 61 with respect to the workpiece clamping module 62 is changed (4) :Axis::The mechanism 5 drives the turning and milling machine to "from the rotating member 53, to> by including the slider 4, the direct 54, wherein: TM and up to 52, and the clutch tooth module Slidingly disposed on the vehicle sharp multi-tasking machine, and arranging the B-axis rotating member 53 to rotate the main shaft by the B-axis rotating member 53; and the clutch-toothing module is disposed in the (four) seat (four) β 2 rotating member Between the two, in order to selectively switch (four) axis rotation of the sliding seat positioning state. One% swallows the direct drive motor 5 2 will 5 Φ 目 ^ π a ... has a motor shovel 523 fixed to the carriage, and the motor rotor 52 that is driven by the motor stator, such as excitation, by the motor The motor 521 is driven to rotate by the excitation of the rotor 521 and the coil of the motor stator 523, and the sub-521 is fixed to the b-axis rotating member %. The clutch gear module 54 has a clutch tooth rotating member 543 fixed to the cymbal rotating member 、, a clutch tooth fixing member 54 fixed to the sliding seat 4, and a switchable contact selectively (4) The clutching member 545 of the clutching member 543 and the clutching tooth fixing member 541 are combined. In the embodiment, the clutch tooth rotating member (4) and the clutch tooth fixing member, (4) are disposed adjacent to each other, and the clutch gear holder 545 is difficult for the clutch tooth rotating member 543 and the clutch tooth fixing member 541. The top can be moved up and down to switch positions. In addition, the clutch sleeve coupling member (10) can be driven to move up and down to switch the position through an oil relay 19856 10 200823005 i. In order to supply the cooling and lubrication required for the milling spindle 61, the pivot position of the B-axis rotating member 53 includes a B-axis oil passage inner ring 53 and a β-axis coaxially fixed to the slider 4 on the outside. The outer loop of the oil passage is used to provide cooling and lubricating oil. In the present embodiment, the oil pressure control provided by the hydraulic pressure circuit 55 is controlled by the clutch gear clutch 545 of the clutch gear module 54 to control, for example, turning or milling the king, control, The clutch gear holder #4 is pressed down to the clutch gear fixing member (4) and the clutch tooth rotating member 543, and the slider 4 is fixed due to the clutch tooth fixing member, and the clutch is fixed. The rotating member (4) is fixed to the μ (four) rotating member 53, so that the clutch rotating member 53 is fixed relative to the sliding seat 4 when the clutching sleeve closing member 545 is downwardly fitted, so that the rotating member 53 can be locked instantly and accurately. The swing function of the cutting spindle 61 is achieved to achieve a fixed angle and to increase the overall rigidity and required precision. On the other hand, the hydraulic clutch is used to control the operation of the clutch sleeve 545 of the clutch gear module 54 to control the oil squeegee to make the clutch sleeve 545 upward when the swing indexing adjustment is performed between turning or milling. The clutch clutch 541 and the clutch gear rotating member 543 are disengaged to disengage the clutch gear holder 545 from the clutch tooth holder 541 and the clutch gear rotating member 5 (the sub-control direct drive motor) 52 exciting driving the shaft rotating member 53 to rotate, opening the swing indexing function of the cutting spindle 61, and realizing the reciprocating swing switching requirement of the continuous machining operation, wherein the design of the spindle driving mechanism 5 constituted by the direct driving motor 52 is It avoids the problem of transmission backlash and the problem of insufficient torque transmission in the prior art, so as to have the advantage of high dynamic precision of high servo pressure of 19856 11 200823005 1 ^. Therefore, the turning and milling composite composed by the invention The processing machine Β shaft drive mechanism can use the direct drive motor to drive the motion system of the load directly from the rotor of the motor, without any speed reduction mechanism or transmission mechanism in the middle of power transmission. It is used for indirect transmission, so it does not cause loss of mechanical efficiency and error between transmission mechanisms. In addition, it has the advantages of no transmission backlash and high servo response. θ Compared with the prior art, the present invention The proposed f-axis drive mechanism of the turning and milling machine, the Xiang clutch module to control the turning and milling capability of the turning and milling joints, the clutch gears of the clutch gear module, the clutch teeth, and the clutch teeth. Rotating moving parts 遂 to achieve the turning and milling angle processing and improve the overall rigidity; reuse clutch gear module clutch # sets: = = off; fixed parts, and clutch teeth rotating parts to achieve the precision of milling continuous swing processing The demand, which will take advantage of the positioning accuracy and processing and make n挟(4)1112::: reduce the time it takes to convert and improve the processing efficiency, has overcome the problems of the prior art. The above embodiment is merely illustrative. The principles of the present invention are not intended to limit the present invention, and any one of the technical fields can be changed without departing from the spirit and scope of the present invention. The protection scope is listed in the scope of application for patents. Feng Ruhou's description of 19856 12 200823005 [Simple description of the diagram] The first diagram is a schematic diagram of the well-known B-axis rotation module; the return drive structure is shown in the figure The β-axis rotation module utilizes a schematic diagram of a worm-gear section; the third section of the turbulent-moving structure is a schematic view of a conventional β-axis rotation module using a rolling force to drive the structure; the drive mechanism section 4 is a turning-milling composite of the present invention. Schematic diagram of the processing machine β; and the brother 5 is a schematic diagram of the turning and milling compound sharpening machine using the β-drive mechanism of the turning and milling machine for the invention. [Main component symbol description] 11 Servo motor 12 Spur gear 13 Sharpening spindle 14 Β shaft module 21 worm 22 worm gear 31 祠 motor 32 spur gear 33 cam 34 Β shaft module 35 follower 351 roller 19856 13 200823005 * - » 4 slide 5 B-axis drive mechanism 52 direct drive motor 521 Motor rotor 523 Motor stator 53 B-axis rotary member 531 B-axis oil passage inner ring 54 Clutch gear module 541 Clutch gear holder 543 Clutch tooth rotation member 545 Clutch gear sleeve A hydraulic circuit 547 the movable member 55 B-axis table 6 oil passage 61 of the outer ring 62 of the workpiece clamping module milling spindle