13024881302488
I k I 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S成’然而加工工具機發展快速且技術不斷 進步，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 。又计優劣則會直接導致加工產品的精度問題以及加工機 的哥命問題，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、 傳動齒背隙在長時間使用後需調整、或不適合做連續加工 籲等問題發生，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i/w州專利EP0899057號所揭示的驅動機構，請參閱 第1圖，即採用伺服馬達u以正齒輪12將動力傳遞於銑 削主軸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 1302488 t k _ 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軸的 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圖該技 術係採用伺服馬達（未圖示）經蝸桿21將動力傳遞於銑 削主軸（未圖示），而此種傳遞動力之方式係與銑削主軸 所組合的B軸模組經從動件堝輪22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，以蝸輪Μ傳 動具有較大的減速能力以及較大的扭矩放大作用，但以蝸 輪22產生之傳動則因齒距較大不適合高速化之傳動，且 蜗輪22傳動之背隙需要經過調整，在長時間使用過後必 須再進行調整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圖所示之歐洲專利EP1647355A1案 _、、t、遂提出&用飼服馬達31先將動力傳遞於正齒輪32 ^速做扭矩放A，再將動力依序傳遞至凸輪33、滾子 51 ’使其透過滾子351肖凸輪％之搭配帶動B轴模組 技術1^用轉運動，是較為複雜的間接驅動系統，由於該 可提供傳輪33輪廊與滾子351之間的滚動摩擦，故 押制It 動力，但由於凸輪33的轉角加工不易 :而==_35^+351與凸輪33之間易於磨 單位，L之^比不一的狀況，因此無法達到最小的進給 、 凸輪33的輪廓製作較為複雜，如何達 19856 6 -1302488 ι ► 到所需之加工精度，仍為需要克服之關鍵技術。 因此，有效解決前揭技術所存在之問題，開發出一具 有直接驅動能力之驅動機構，將直接驅動的效果直接傳到 負載並避免經過傳動變速機構以提高定位精度及加工精 度’實為目前所亟待解決之課題。 ^ 【發明内容】 鑒於以上所述先前技術之缺點，本發明之主要目的即 在於提供一種車銑複合加工機B軸驅動機構，俾提升定位 _精度及加工精度。 本發明之次要目的在於提供一種車銑複合加工機b 軸驅動機構，俾利於連續加工作業，提高加工效率。 為達上揭目的以及其他目的，本發明提供一種車銑複 合加工機B轴驅動機構，係應用於驅動車銑複合加工 B軸旋轉動件’至少包括：滑座，係滑動設置於該車銳複 合加工機上，並供轉動配置該B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I k I 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. All the processing and manufacturing considerations required for plane accuracy, workpiece thickness accuracy, etc. must use various processing machine tools to assist S into the process. However, the processing machine is developing rapidly and technically. Continuous improvement, such as lathe processing machines have been developed from traditional conventional lathes, CNC (computer numerical control) lathes to multi-axis, high-speed, and high-precision turning and milling composite models, processing under these improved progress Machine tool. The advantages and disadvantages will directly lead to the accuracy of the processed products and the fate of the processing machine. For example, in machining, in the machining methods such as milling and turning, if the machine parts of the processing machine are not properly designed, it is easy to have insufficient torque and drive. The backlash of the tooth needs to be adjusted after a long time of use, or is not suitable for continuous processing and so on. If it needs several adjustments after use, the original machining accuracy can be restored, which also causes great inconvenience. For example, in the driving mechanism disclosed in the Japanese Patent No. EP0899057, please refer to FIG. 1 , that is, the servo motor u is used to transmit the power to the milling spindle 13 with the spur gear 12, and the way of transmitting the power is the same as the milling spindle 13 The combined B-axis 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 transmission speed of the spur gear 12 is relatively small. The high torque output 'is relatively unsuitable for continuous machining applications, and the spur gear 5 19856 1302488 tk _ 12 is not easy to adjust during installation, and the adjustment accuracy is not easy after machining, so it is difficult to eliminate the backlash of the transmission teeth. Not suitable as a drive mechanism for the B axis. In view of the fact that the prior art cannot provide a large torque output problem, the Japanese patent JP2001322001 proposes to overcome the technique. Please refer to Fig. 2. This technique uses a servo motor (not shown) to transmit power to the milling spindle via the worm 21 (not shown). And the B-axis module combined with the milling spindle is driven by the driven wheel 22 to indirectly drive the system to generate a rotary motion. Compared with the driving mechanism using the gear, the worm gear transmission has a higher Large deceleration capability and 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 worm gear 22 needs to be adjusted, and must be carried out after long-term use. Adjustments to maintain better transmission accuracy are very inconvenient. ...to solve the problem of the transmission backlash of the prior art and the inability to have a large torque output, as in the case of the European patent EP1647355A1 shown in Fig. 3, _, t, 遂 proposed & The spur gear 32 speeds the torque to put A, and then the power is transmitted to the cam 33 and the roller 51' in sequence, so that the B-axis module technology is used to drive the B-axis module technology through the roller 351. The indirect drive system, because it can provide the rolling friction between the wheel 33 and the roller 351, the It power is pressed, but the corner processing of the cam 33 is not easy: and ==_35^+351 and the cam 33 It is easy to grind the unit, and the ratio of L is different. Therefore, the minimum feed cannot be achieved, and the contour of the cam 33 is more complicated. How to reach the required machining accuracy of 19856 6 -1302488 ι ► still needs to be overcome Key technology. Therefore, effectively solve the problems existing in the prior art, develop a drive mechanism with direct drive capability, directly transfer the direct drive effect to the load and avoid passing the transmission shifting mechanism to improve the positioning accuracy and machining accuracy. Urgent issues 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 B-axis driving mechanism for a turn-milling machine for improving the positioning accuracy and machining accuracy. A secondary object of the present invention is to provide a b-axis driving mechanism for a turning and milling machine for machining, which facilitates continuous machining operations and improves machining efficiency. In order to achieve the above and other objects, the present invention provides a B-axis driving mechanism for a turning and milling machine, which is applied to a drive-milling composite machining B-axis rotating member' at least comprising: a sliding seat, which is slidably disposed on the vehicle sharp The B-axis rotating member is disposed on the composite processing machine; the direct driving horse_, has at least a motor stator fixed to the sliding seat, and the motor
定子激磁而驅轉之馬達轉子，且該馬達轉子並固定至該Ba stator that is excited to drive the motor rotor, and the motor rotor is fixed to the B
軸方疋轉動件，以及離合齒模組，係配置於該滑座與該B 轴旋轉動件之間，以供選擇性地切換該B軸旋轉動件與該 滑座之定位狀態。 、Λ 前述本發明之加工機Β軸旋轉機構車銑複合加工機Β 軸驅動機構中，該離合齒模組係可包括固定至該Β軸旋轉 動件之離合齒旋轉動件、固定至該滑座之離合齒固定件、 以及可切換位置而選擇性地同時嚙合該離合齒旋轉動件 19856 7 1302488 i % 及離合齒固定件之離合齒套合動件。較佳地，該離合齒旋 轉動件及該離合齒固定件係可相鄰配置，而該離合齒套合 動件則位於該離合齒旋轉動件及離合齒固定件之上方可 上下運動以切換位置。此外，該離合齒套合動件係可透過 一油壓迴路驅動上下運動以切換位置。 所述之驅動機構復可包括設於該B軸旋轉動件之外 緣與該滑座之間的軸承，特別係一高精度軸承，其中，該 间精度轴承係與B轴旋轉動件共軸，並設置於該B軸旋轉 動件之外緣，以供支撐B軸旋轉動件，較佳地，該高精度 軸承復提供B軸轉動之精度，換言之，該β軸旋轉動件藉 由高精度軸承之配置，將直接驅動馬達直接傳遞之動力曰， 提升為更具精度之傳動力。 另外’本發明之加工機B軸旋轉機構車銑複合加工機 B軸驅動機構，復可包括固定於該滑座上以回授提昇直接 驅動馬達之驅動精度之編碼器，特別係一高精度編碼器， 鲁其係供直接驅動馬達傳動精度之提升。 該B轴旋轉動件之轴心位置係包括—B軸油路内環 :其外部則可設有同軸固定於該滑座上之B軸油路外< 環’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㈣軸驢動機 構’主要係包括滑座、設於滑座上之直接驅動馬達、以及 選擇性地切換該B軸旋轉動件與該滑座之定位狀態的離 合齒模組，俾達成車銑之精度f求並提升整 體剛性，復利用離合齒模組之離合齒套合動件向上脫離離 19856 1302488 -合齒固定件、及離合齒旋轉動件達成銑削持續擺動加工時 之精度需求，如此將利用直接驅動之動力源提升定位 及加工精度且使工件一次挾持後即可完成所有工序，減少 製程轉換所耗費之時間，並提高加工效率，解決先前技術 所存在之問題。 【實施方式】 以下茲配合圖式說明本創作之具體實施例，以使所屬 技術中具有通常知識者可輕易地瞭解本創作之技術特徵 着與達成功效。 請參閱第4圖，係為本發明車銑複合加工機β轴驅動 機構剖面示意圖，如圖所示車銳複合加工機之驅動機 構5,係應用於驅動車銑複合加工機之B軸旋轉動件， 主要係於一供轉動配置該B軸旋轉動件53之滑座4上讯 有直接驅動馬達52與離合齒模組54，該直接驅動馬達= 係用以直接驅轉該B軸旋轉動件53,而該離合齒模組“ _則係，選擇性地切換該B軸旋轉動件53與該滑座4之定 =狀心纟於&用直接驅動設計，故具備高動態精度及零 專動背隙等優點，而無機械效應上的損失，並利於連續二 工之應用。 、 -二配合參閱第4圖及第5圖，本發明所指B軸驅動機 *係應用於車銑複合加工機中，所屬技術領域中具有通 吊知識者應均可了解所謂之B軸係泛指前述之滑座4、β 以及轉動件53等所構成之整體， 載車銳複合加工機之銑削主軸6卜並藉由適當角 19856 9 1302488 度的轉動提供相對於該銑削主軸61的分度作用，亦即在 利用該賴主軸61進行連續加工作業之巾，貞責 銑削主軸61相對於工件夹持模組62之角度變化。^ Β軸驅動機構5驅動車銑複合加工機之Β軸旋轉動件 53，至少由包括滑座4、直接 54，其中： 直接驅動馬達52、及離合齒模組 該滑座4係滑動設置於該車銑複合加卫機上，並 動配置該Β軸旋轉動件53，以藉該6軸旋轉動件Μ承载 鲁銑削主軸61 ;以及離合齒模組，係配置於該滑座㈣β 轴旋轉動件之間，以供選擇性地切換該3轴旋轉動件鱼該 滑座之定位狀態。 ' —該直接驅動馬達52係至少具有固定於該滑座之馬達 定子523、及藉由該馬達定子523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，且該馬達轉 鲁子521並固定至該β軸旋轉動件53。 該離合齒模組54係具有固定至該Β軸旋轉動件53 之離合齒旋轉動件543、固定至該滑座4之離合齒固定件 54卜以及可切換位置而選擇性地同時嚙合該離合齒旋轉 動2 543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543及該離合齒固定件 541係相鄰配置，而該離合齒套合動件545則位於該離合 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545係可透過一油壓 19856 10 1302488 1 > 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㈣旋 轉動件53之軸心位置包括一 B軸油路内環53ι，其外部 ，設有同軸固定於該滑座4上之B轴油路外環55，用以 提供冷卻及賴油路。於本實_中，係制油壓迴路 55所提供之油壓控制離合齒模組54之離合齿套合動件 545的作動，以使欲進行例如車削或銑削加工時，控制、由 壓使該離合齒套合動件545向下唾合該離合齒固定件⑷ 及該離合齒旋轉動件543’由於該離合齒固定件541係與 該滑座4相岐，且該離合齒旋轉動件⑷係與該β轴旋 轉動件53相固定，故使離合齒套合動件545向下嚙合時 將該B軸旋轉動件53與該滑座4相對固定，故可即^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。 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二調 整時，控制油壓使離合齒套合動件545向上脫離離合=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^ 之嚙合’並控制直接驅動馬達52激磁驅動該Β軸旋轉動 件53旋轉，開啟切削主軸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= 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 -1302488The pivoting member and the clutching gear module are disposed between the sliding seat and the B-axis rotating member for selectively switching the positioning state of the B-axis rotating member and the sliding seat. Λ In the above-mentioned processing machine, the shaft rotating mechanism of the turning and milling mechanism of the present invention, the clutch gear module may include a clutch gear rotating member fixed to the shaft rotating member, and fixed to the sliding The clutch teeth fixing member and the switchable position selectively engage the clutch tooth rotating member 19856 7 1302488 i % and the clutch tooth holder of the clutch tooth fixing member. Preferably, the clutch gear rotating member and the clutch tooth fixing member are adjacently disposed, and the clutch gear sleeve moving member is located above the clutch tooth rotating member and the clutch tooth fixing member to be movable up and down to switch position. In addition, the clutch sleeve mover is driven to move up and down through a hydraulic circuit to switch positions. The driving mechanism may further include a bearing disposed between the outer edge of the B-axis rotating member and the sliding seat, in particular a high-precision bearing, wherein the precision bearing is coaxial with the B-axis rotating member And disposed on the outer edge of the B-axis rotating member for supporting the B-axis rotating member. Preferably, the high-precision bearing provides the accuracy of the B-axis rotation. In other words, the β-axis rotating member is high. The precision bearing configuration will directly drive the power transmitted directly by the motor to a more precise transmission force. In addition, the B-axis driving mechanism of the B-axis rotating mechanism turning and milling machine of the processing machine of the present invention may include an encoder fixed on the sliding seat to feedback the driving precision of the direct driving motor, in particular, a high-precision coding. , Lu Qi is for the direct drive motor drive accuracy. The axial position of the B-axis rotating member includes a B-axis oil passage inner ring: the outside thereof may be provided with a B-axis oil passage coaxially fixed to the sliding seat. The ring is used for providing cooling and lubricating oil. road. The turning and milling combined machining (four) shaft sliding mechanism proposed by the present invention mainly comprises a sliding seat, a direct driving motor provided on the sliding seat, and selectively switching the positioning state of the B-axis rotating member and the sliding seat. The clutch gear module achieves the precision of turning and milling and improves the overall rigidity. The clutch sleeve of the clutch module is used to disengage upwardly from the 19856 1302488 - the toothed fixing member and the clutch tooth rotating member The precision requirement for milling continuous oscillating machining, so that the direct drive power source can be used to improve positioning and machining accuracy, and all the processes can be completed after the workpiece is held once, the time required for process conversion is reduced, and the processing efficiency is improved, and the prior art is solved. The problem that exists. [Embodiment] Hereinafter, specific embodiments of the present invention will be described with reference to the drawings so that those skilled in the art can easily understand the technical features of the present invention and achieve the effects. Please refer to Fig. 4, which is a schematic cross-sectional view of the β-axis driving mechanism of the turning and milling compound processing machine of the present invention. The driving mechanism 5 of the car-shaping composite processing machine is used to drive the B-axis rotating motion of the turning and milling machine. The main driving system 52 is provided with a direct drive motor 52 and a clutch gear module 54 for directly rotating the B-axis rotary motion. And the clutch gear module " _ is selected to selectively switch the B-axis rotating member 53 and the sliding seat 4 to be in the shape of a direct drive design, thus having high dynamic accuracy and Zero special motion backlash and other advantages, without loss of mechanical effect, and is conducive to the application of continuous two-work. - - 2 with reference to Figure 4 and Figure 5, the B-axis drive machine of the present invention is applied to the vehicle In the milling and compounding machine, those skilled in the art can understand that the so-called B-axis system generally refers to the above-mentioned sliding seat 4, β and the rotating member 53 and the like, and the vehicle-carrying composite processing machine Milling the spindle 6 and providing relative rotation by the appropriate angle of 19856 9 1302488 degrees The indexing action of the milling spindle 61, that is, the towel for continuous machining operation by the spindle 61, is responsible for the change of the angle of the milling spindle 61 with respect to the workpiece clamping module 62. ^ The spindle drive mechanism 5 drives the milling The boring shaft rotating member 53 of the composite processing machine includes at least a sliding seat 4 and a direct unit 54, wherein: the direct driving motor 52 and the clutching tooth module are slidably disposed on the turning and milling compounding machine. And arranging the cymbal rotating member 53 to carry the boring spindle 61 by the 6-axis rotating member ;; and the clutching tooth module is disposed between the sliding seat (four) β-axis rotating member for selective The positioning state of the slider of the 3-axis rotary member is switched. The direct drive motor 52 has at least a motor stator 523 fixed to the carriage, and a motor rotor driven by the motor stator 523 to be driven by the motor stator 523 The motor rotor 521 is driven to rotate by the excitation of the coils of the motor rotor 521 and the motor stator 523, wherein the motor is rotated and fixed to the β-axis rotary member 53. The clutch tooth mold Group 54 has a fixed to the Β a clutch tooth rotating member 543 of the rotating member 53, a clutch tooth fixing member 54 fixed to the sliding seat 4, and a switchable position to selectively simultaneously engage the clutch tooth rotating motion 2 543 and the clutch tooth fixing member 541. In the present embodiment, the clutch gear rotating member 543 and the clutch tooth fixing member 541 are disposed adjacent to each other, and the clutch sleeve clutch member 545 is located at the clutch gear rotating member 543. The clutch gear 541 can be moved up and down to switch the position. In addition, the clutch gear clutch 545 can be driven by a hydraulic pressure 19856 10 1302488 1 > In order to supply the cooling and lubrication required for the milling spindle 61, the axial position of the (four) rotating member 53 includes a B-axis oil passage inner ring 53i, and the outside thereof is provided with a B-axis oil coaxially fixed to the sliding seat 4. The outer ring 55 is used to provide cooling and oil passage. In the present embodiment, the oil pressure control circuit 55 provided by the hydraulic circuit 55 controls the operation of the clutch gear clutch 545 of the clutch gear module 54 to control and pressurize when, for example, turning or milling is to be performed. The clutch gear holder 545 is slid down to the clutch tooth fixing member (4) and the clutch tooth rotating member 543'. The clutch tooth fixing member 541 is opposite to the sliding seat 4, and the clutch tooth rotating member (4) is fixed to the β-axis rotating member 53, so that the B-axis rotating member 53 and the sliding seat 4 are relatively fixed when the clutch-toothed clutch 545 is engaged downward, so that the locking can be accurately and accurately The swing function of the cutting spindle 61 is achieved, and the angle is added to meet the demand', and the overall rigidity and required precision can be improved. On the other hand, the hydraulic clutch is used to control the operation of the clutch sleeve closing member 545 of the clutch gear module 54 to control the oil pressure to make the clutch sleeve clutch member 545 upward when the swing is adjusted between turning or milling. Disengagement clutch=fixing member 541 and clutch tooth rotating member 543, so that the clutching toothed clutch 545 is disengaged upwardly from the clutching tooth fixing member 541 and the clutching gear, and controlling the direct driving motor 52 to drive the motor The rotation of the boring shaft 53 rotates to open the swing indexing function of the cutting spindle 61, thereby realizing the reciprocating oscillating switching requirement of the continuous machining operation, wherein the design of the cymbal drive mechanism 5 constituted by the direct drive = up to 52 can be avoided. The problem of transmission backlash and the problem of insufficient torque transmission in technology, with high servo 19856 11 -1302488
l ^ 4 I " 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B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。 相較於習知技術，本發明所提出之車銑複合加工機B 鲁軸驅動機構，利用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齒固定 件、及離合齒旋轉動件遂達成車銑定角度加工時之精度需 求並提升整體剛性；復利用離合齒模組之離合齒套合動件 向上脫離離合齒固定件、及離合齒旋轉動件達成銑削持續 擺動加工時之精度需求，如此將利用直接驅動之動力源提 升定位精度及加工精度且使工件一次挾持後即可完成所 Φ有工序，減少製成轉換所耗費之時間，並提高加工效率， 相對已克服先前技術所存在之問題。 上述實施例僅例示性說明本發明之原理及其功效，而 非用於限制本發明。任何所屬技術領域中具有通常知識者 句ΊΓ在不运$本發明之精神及範轉下，對上述實施例進行 修飾與改變。因此，本發明之權利保護範圍，應如後述之 申請專利範圍所列。 19856 12 1302488 t » y , “【圖式簡單說明] 一第圖係為白知β軸旋轉模組利用正齒輪驅動結構剖 面不意圖， 第圖係為^知Β軸旋轉模組利用蜗輪堝桿驅動結構 剖面示意圖； 第3圖係為習知β軸旋轉模組利用滾子凸輪驅動結構 侧面示意圖； _第4圖係為本發明車銑複合加工機β軸驅動機構剖面 •示意圖；以及 第5圖係為本發明應用有車銑複合加工機β軸驅動機 構的車銑複合銑削加工機示意圖。 【主 要元件符號說明】 11 伺服馬達 12 正齒輪 13 銳削主轴 14 Β軸模組 21 蝸桿 22 蜗輪 31 伺服馬達 32 正齒輪 33 凸輪 34 Β軸模組 35 從動件 351 滾子 13 19856 1302488 V » -4 滑座 5 B轴驅動機構 52 直接驅動馬達 521 馬達轉子 523 馬達定子 53 B軸旋轉動件 531 B轴油路内環 54 離合齒模組 ❿541 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l ^ 4 I " The service responds to the advantages of extremely high dynamic accuracy. Therefore, the B-axis drive mechanism of the turning and milling machine formed by the present invention can directly drive the motion system of the load by the rotor of the motor by using the direct drive motor, and does not need any speed reduction mechanism or transmission mechanism for indirect transmission. Therefore, there is no loss of mechanical efficiency and error between the transmission mechanisms. In addition, it has the advantages of no transmission backlash and high servo response. Compared with the prior art, the B-axis drive mechanism of the milling and milling machine of the present invention utilizes a clutch-tooth module to control the milling and milling capability, and the clutch-tooth clutch of the clutch-tooth module is oriented. The lower meshing clutch tooth fixing member and the clutch tooth rotating member 遂 achieve the precision requirement of the milling and milling angle processing and improve the overall rigidity; the clutch clutch sleeve of the composite clutch module is separated upwardly from the clutch gear fixing member, and The clutch tooth rotating member achieves the precision requirement for the continuous swinging operation of the milling, so that the direct driving power source can be used to improve the positioning accuracy and the machining precision, and the workpiece can be completed after the workpiece is clamped once, thereby reducing the cost of the conversion. Time, and improve processing efficiency, has overcome the problems of the prior art. The above-described embodiments are merely illustrative of the principles of the invention and its effects, and are not intended to limit the invention. Modifications and variations of the above-described embodiments are possible without departing from the spirit and scope of the invention. Therefore, the scope of protection of the present invention should be as set forth in the appended claims. 19856 12 1302488 t » y , "[Simple diagram] The diagram is for the purpose of the β-axis rotation module using the spur gear to drive the structure profile. The figure is for the Β Β axis rotation module using the worm wheel mast Schematic diagram of the driving structure; Fig. 3 is a schematic side view of the conventional β-axis rotating module using the roller cam driving structure; _ 4 is a sectional view of the β-axis driving mechanism of the turning and milling machine of the present invention; and 5th The drawing is a schematic diagram of the turning and milling compound milling machine using the β-axis driving mechanism of the turning and milling machine for the invention. [Main component symbol description] 11 Servo motor 12 Spur gear 13 Sharpening spindle 14 Clamping shaft module 21 Worm 22 Worm gear 31 Servo motor 32 Spur gear 33 Cam 34 Clamping shaft module 35 Follower 351 Roller 13 19856 1302488 V » -4 Sliding seat 5 B-axis drive mechanism 52 Direct drive motor 521 Motor rotor 523 Motor stator 53 B-axis rotary mover 531 B-axis oil passage inner ring 54 clutch gear module ❿ 541 clutch gear holder 543 clutch gear rotation member 545 clutch gear sleeve coupling member 547 hydraulic circuit 55 B-axis oil passage outer ring 6 bed 61 62 $ milling spindle workpiece holding module