JP2012192481A - Spindle driving device - Google Patents
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- JP2012192481A JP2012192481A JP2011057875A JP2011057875A JP2012192481A JP 2012192481 A JP2012192481 A JP 2012192481A JP 2011057875 A JP2011057875 A JP 2011057875A JP 2011057875 A JP2011057875 A JP 2011057875A JP 2012192481 A JP2012192481 A JP 2012192481A
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Abstract
Description
本発明は、ギヤシェーパ等の割出回転及び往復運動機構を有し、さらに穴や筒等の高速回転加工が可能な複合工作機械の主軸駆動装置に関する。 The present invention relates to a spindle driving device for a complex machine tool having an indexing rotation and reciprocating motion mechanism such as a gear shaper and capable of high-speed rotation processing such as holes and cylinders.
従来、回転と割出しを有する工作機械の一つに、ギヤシェーパがある。例えば特許文献１の図１のギヤシェーパでは、主軸先端にピニオンカッタを取付け、主軸に設けられた従動歯車を割出用駆動モータで回転させると同時に、球面軸受を介してクランク機構を主軸に接続し、主軸を上下に移動させ、歯車を製作している。なお、往復動作の往復動（中心）位置は、主軸全体を上下動する。さらには、ＮＣ工作機械の進歩により、特許文献２のようなマシニングセンタでは、ワークを載置又は固定するテーブル、あるいは工具が取付けられる工具主軸において割出機能の他に、ワークの穴加工等の高速回転ができるものが増加している。しかし、生産効率や精度の点で専用機より劣るという問題があった。 Conventionally, there is a gear shaper as one of machine tools having rotation and indexing. For example, in the gear shaper of FIG. 1 of Patent Document 1, a pinion cutter is attached to the tip of the main shaft, and a driven gear provided on the main shaft is rotated by an indexing drive motor, and at the same time, a crank mechanism is connected to the main shaft through a spherical bearing. The gear is made by moving the main shaft up and down. The reciprocating (center) position of the reciprocating operation moves up and down the entire main shaft. Furthermore, with the advancement of NC machine tools, in machining centers such as Patent Document 2, a table for placing or fixing a workpiece, or a tool spindle to which a tool is attached, in addition to an indexing function, high-speed drilling of workpieces, etc. The number that can rotate is increasing. However, there is a problem that it is inferior to a dedicated machine in terms of production efficiency and accuracy.
そこで、ＮＣ旋盤等の複合工作機械では、精度を確保するために、割出用モータ（サーボモータ等）と高速回転用モータ（スピンドルモータ等）とを設けて、クラッチ等により主軸と各モータとを選択的に接続し、割出又は高速回転を行っている。例えば特許文献２の自動旋盤においては、回転と割出を主軸後端に配置された切換機構を前後させることにより選択している。主軸の後端側にはクラッチコーンとスプラインが形成され、さらに、切換機構及び高速回転用モータによりプーリ駆動される回転伝動軸が配置されている。切換機構は先端側にクラッチコーンと外周に外歯車を有し、前進時には、クラッチコーンに接続され、かつ外歯車は割出用モータに接続された割出機構にかみ合うようにされている。これにより割出を行う。また、切換機構は後端に主軸とスプライン嵌合し後側に延出するスプライン穴を有し、後退時には、回転伝達軸のスプラインと嵌合し、主軸を高速回転するようにしている。 Therefore, in a complex machine tool such as an NC lathe, an indexing motor (servo motor, etc.) and a high-speed rotation motor (spindle motor, etc.) are provided in order to ensure accuracy. Are selectively connected to perform indexing or high-speed rotation. For example, in the automatic lathe of Patent Document 2, the rotation and the indexing are selected by moving the switching mechanism arranged at the rear end of the spindle back and forth. A clutch cone and a spline are formed on the rear end side of the main shaft, and a rotation transmission shaft driven by a pulley by a switching mechanism and a high-speed rotation motor is disposed. The switching mechanism has a clutch cone on the distal end side and an external gear on the outer periphery, and is connected to the clutch cone when moving forward, and the external gear is engaged with an indexing mechanism connected to an indexing motor. Thus, indexing is performed. Further, the switching mechanism has a spline hole that is spline-fitted with the main shaft at the rear end and extends rearward, and when retracted, the switching mechanism is fitted with the spline of the rotation transmission shaft so that the main shaft rotates at high speed.
一方、このような割出機構を有する工作機械では割出精度が要求される。しかし、割出は駆動軸から、複数の歯車を介して回転テーブル軸や工具主軸に伝達されるので、歯車によるバックラッシのため、割出精度が低下する。 On the other hand, a machine tool having such an indexing mechanism requires indexing accuracy. However, since indexing is transmitted from the drive shaft to the rotary table shaft and the tool spindle via a plurality of gears, the indexing accuracy is reduced due to backlash by the gears.
そこで、特許文献３の図１においては、テーブル回転用であるが、バックラッシを少なくするために、図７に示すようなバックラッシ調整装置８１を用いている。このバックラッシ調整装置は、ターニングテーブル２駆動用であり、駆動軸９０を軸方向移動させることにより、割出と高速回転とを切り替えることができるようにされている。図７は高速回転時を示す。 Therefore, in FIG. 1 of Patent Document 3, although for table rotation, in order to reduce backlash, a backlash adjusting device 81 as shown in FIG. 7 is used. This backlash adjusting device is for driving the turning table 2 and can switch between indexing and high-speed rotation by moving the drive shaft 90 in the axial direction. FIG. 7 shows the high-speed rotation.
駆動用の駆動平歯車９１を駆動軸９０に設け、この駆動平歯車にかみ合う第１の平歯車９２と、この第１平歯車と同軸に第２のはすば歯車９４を設けて第１の中間軸８５とする。さらに、第１平歯車９２とは別に、駆動平歯車９１と、かみ合う第３の平歯車９５と、この第３の平歯車と同軸に第４のはすば歯車９７を設けて第２中間軸８６とする。そして、第２、第４のはすば歯車９４、９７をテーブル回転軸６ｃ（主軸）の従動はすば歯車１８に同時にかみ合うようにされている。さらに、第１又は第２中間軸８５、８６の少なくとも一方を軸方向に移動させることにより、従動はすば歯車１８（主軸２）と駆動はすば歯車９１間のバックラッシを調整できる。 A drive spur gear 91 for driving is provided on the drive shaft 90, a first spur gear 92 that meshes with the drive spur gear, and a second helical gear 94 that is coaxial with the first spur gear are provided. The intermediate shaft 85 is used. Further, in addition to the first spur gear 92, a driving spur gear 91, a third spur gear 95 to be engaged, and a fourth helical gear 97 are provided coaxially with the third spur gear to provide a second intermediate shaft. 86. The second and fourth helical gears 94 and 97 are engaged with the helical gear 18 at the same time as the follower of the table rotation shaft 6c (main shaft). Further, the backlash between the driven helical gear 18 (main shaft 2) and the driving helical gear 91 can be adjusted by moving at least one of the first or second intermediate shafts 85 and 86 in the axial direction.
割出は駆動軸を下方（矢印）に移動させ、駆動平歯車９１に、第１の平歯車９２と第３の平歯車９５をかみ合わせる。同時にクラッチ１０５を働かせウォームギヤ１０２と駆動軸９０を接続する。図示しない割出用モータでウォームギヤを駆動し、バックラッシを防止しながら割出を行う。さらに、高速回転では、図５に示すように、駆動軸９０を上昇させ、バックラッシ調整機能を解除した状態で高速用駆動モータ１０３により高速回転をおこなう。 In indexing, the drive shaft is moved downward (arrow), and the first spur gear 92 and the third spur gear 95 are engaged with the drive spur gear 91. At the same time, the clutch 105 is operated to connect the worm gear 102 and the drive shaft 90. The worm gear is driven by an indexing motor (not shown) to perform indexing while preventing backlash. Further, in the high-speed rotation, as shown in FIG. 5, the drive shaft 90 is raised and the high-speed drive motor 103 performs high-speed rotation in a state where the backlash adjustment function is released.
しかし、特許文献１では、主軸用駆動モータは１つなので、割出精度と高速の両方を満足させるモータは一般に入手は困難で、コストが高く、制御も複雑になるという問題があった。また、特許文献１のギヤシェーパの軸の上下運動と、特許文献３又は４の割出及び高速回転軸とを一体にしたものはなかった。さらに、特許文献１を特許文献３に適用するためには、剛性向上のために主軸の軸方向長さを確保する必要があり、さらに軸方向に長くしなければならない。また、特許文献１を特許文献４に適用しても、特許文献４のものは、ターニングテーブル用であり、穴加工の主軸のような高速回転を得ることは困難である。また、高速回転時には従動はすば歯車１８（主軸２）は第４のはすば歯車９７とかみ合えばよいが、第２のはすば歯車９４ともかみ合っているので負荷が多くなり、また、歯車抵抗が増すという問題があった。さらに、両者とも往復動作機構と割出用及び高速回転用モータを前後移動する切換機構の両機能を配置するために構造が複雑、大きくなるという問題があった。 However, in Patent Document 1, since there is one main shaft drive motor, there is a problem that a motor that satisfies both indexing accuracy and high speed is generally difficult to obtain, is expensive, and is complicated to control. Further, there was no one in which the vertical movement of the shaft of the gear shaper of Patent Document 1 and the indexing and high-speed rotation shaft of Patent Document 3 or 4 were integrated. Furthermore, in order to apply Patent Document 1 to Patent Document 3, it is necessary to ensure the axial length of the main shaft in order to improve rigidity, and it is necessary to make it longer in the axial direction. Moreover, even if patent document 1 is applied to patent document 4, the thing of patent document 4 is for turning tables, and it is difficult to obtain high-speed rotation like the main axis of drilling. Further, the driven helical gear 18 (main shaft 2) may be engaged with the fourth helical gear 97 during high-speed rotation, but the second helical gear 94 is also engaged with the second helical gear 94. There was a problem that the gear resistance increased. Furthermore, both have a problem that the structure is complicated and large because both functions of the reciprocating mechanism and the switching mechanism for moving the indexing and high-speed rotating motor back and forth are arranged.
かかる問題点に鑑みて、本発明の課題は、モータ切換機構及び往復動機構を複雑化せず小型で簡単な、穴加工等の高速回転と割出回転が可能な主軸駆動装置を提供することである。さらには、一般の穴加工等の回転加工とギヤシェーパ加工等の往復動加工を精度よく効率的に行える主軸駆動装置を提供することである。 In view of such problems, an object of the present invention is to provide a spindle driving device capable of high-speed rotation and indexing rotation such as drilling without complicating the motor switching mechanism and the reciprocating mechanism. It is. Furthermore, another object is to provide a spindle drive device that can perform rotation processing such as general hole processing and reciprocating processing such as gear shaper processing with high accuracy and efficiency.
本発明においては、工作機械等の回転軸の駆動装置において、前記回転軸は、主軸台に転がり軸受で支持された中空高速軸と、前記中空高速軸内両端から突出しかつ前記中空高速軸内を滑り軸受で回転かつ軸方向に摺動可能に挿通され先端に工具を取付け可能にされた主軸と、を備え、前記主軸は前記主軸の後端側に設けられ前記主軸とは軸方向に摺動可能にかつ前記主軸と一体に回転する従動歯車を有し、前記中空高速軸の軸端に設けられ前記主軸の軸方向移動に伴って前記中空高速軸と前記主軸とを回転方向に切断又は接続可能とするクラッチと、を有し、前記クラッチの断続ができるように前記主軸を軸方向に往復動させる往復移動機構と、を備えた主軸駆動装置を提供することにより前述した課題を解決した。 In the present invention, in the drive device for the rotary shaft of a machine tool or the like, the rotary shaft includes a hollow high-speed shaft supported by a rolling stock on a headstock, and projecting from both ends of the hollow high-speed shaft and passing through the hollow high-speed shaft. A main shaft which is inserted in a slide bearing so as to be rotatable and slidable in the axial direction, and to which a tool can be attached at the tip, and the main shaft is provided on the rear end side of the main shaft and slides in the axial direction with the main shaft A driven gear that is capable of rotating integrally with the main shaft and is provided at the shaft end of the hollow high-speed shaft, and the hollow high-speed shaft and the main shaft are cut or connected in the rotational direction as the main shaft moves in the axial direction. The above-described problems have been solved by providing a main shaft driving device that includes a reciprocating mechanism that includes a clutch that enables the main shaft to reciprocate in an axial direction so that the clutch can be engaged and disengaged.
即ち、中空高速軸内に回転及び往復運動可能な主軸を設けた二重構造とし、中空高速軸内両端から突出するように主軸を設けるので、軸方向長さが長くとれる。高速回転時は、主軸と中空高速軸とを軸端のクラッチで結合し、転がり軸受で支持された中空高速軸と主軸を一体に回転させる。一方、割出し時は、主軸と中空高速軸とをクラッチで切離し、従動歯車により主軸を割出回転する。また、主軸は中空高速軸内で滑り軸受により支持されているので、主軸を軸方向に移動させることにより、クラッチの入り切りを行えるので、往復移動機構の構造が簡単である。 That is, since the main shaft is provided so as to protrude from both ends of the hollow high-speed shaft, the main shaft can be rotated and reciprocated in the hollow high-speed shaft, and the axial length can be increased. During high-speed rotation, the main shaft and the hollow high-speed shaft are coupled by a clutch at the shaft end, and the hollow high-speed shaft supported by the rolling bearing and the main shaft are rotated together. On the other hand, at the time of indexing, the main shaft and the hollow high-speed shaft are separated by a clutch, and the main shaft is indexed and rotated by the driven gear. In addition, since the main shaft is supported by the slide bearing in the hollow high-speed shaft, the clutch can be turned on and off by moving the main shaft in the axial direction, so that the structure of the reciprocating mechanism is simple.
さらに、請求項２に記載の発明においては、前記往復移動機構を前記主軸の軸方向の往復動及び前記クラッチの断続ができるようにした。主軸は中空高速軸内で滑り軸受により支持されているので、クラッチの入り切りに加え、往復動機構により軸方向に移動でき、割出及び軸方向往復作動ができる。主軸の軸方向の往復動は従来の往復動機構の場合でも、往復動機構全体を移動できるようにしたり、連結棒の長さを変化できるようにすれば、ギヤシェーパ時の往復作動と、中空高速軸と主軸とを断続するクラッチの操作を容易に兼ねることができる。 Furthermore, in the invention described in claim 2, the reciprocating mechanism is configured to be capable of reciprocating in the axial direction of the main shaft and interrupting the clutch. Since the main shaft is supported by a slide bearing in the hollow high-speed shaft, it can be moved in the axial direction by a reciprocating mechanism in addition to turning on and off the clutch, and can be indexed and reciprocated in the axial direction. The reciprocation of the main shaft in the axial direction is possible even when using a conventional reciprocating mechanism, so that the entire reciprocating mechanism can be moved or the length of the connecting rod can be changed. The operation of the clutch for intermittently connecting the shaft and the main shaft can be easily performed.
また、請求項３に記載の発明においては、前記従動歯車は割出用駆動モータに接続可能にされ、前記中空高速軸は高速回転用モータに接続可能とした。これにより、割出回転時は割出用駆動モータを用い、穴加工等では高速回転用モータを用いることができる。また、請求項３に記載の発明においては、前記従動歯車はバックラッシを防止するバックラッシ調整装置に接続されており、前記割出用駆動モータとは切断又は接続可能にした。 According to a third aspect of the present invention, the driven gear is connectable to an indexing drive motor, and the hollow high-speed shaft is connectable to a high-speed rotation motor. Thus, an indexing drive motor can be used during indexing rotation, and a high-speed rotation motor can be used for drilling or the like. According to a third aspect of the present invention, the driven gear is connected to a backlash adjusting device that prevents backlash and can be disconnected or connected to the indexing drive motor.
さらに、請求項５に記載の発明においては、前記往復動機構は、前記主軸後端に回転自在に接続された懸架部材と、前記懸架部材を上下移動可能に保持するリニア軸受と、前記懸架部材をリニア軸受にクランプ又はアンクランプする懸架部材クランプ装置と、前記懸架部材に接続されるクランク機構と、前記クランク機構の偏心量を調整するクランクピン取付部材と、前記クランク機構を駆動する駆動モータを設けた。クランク軸で上下される懸架部材を懸架部材クランプ装置により固定することができる。これによりクラッチの断続（入切）を行う。 Furthermore, in the invention according to claim 5, the reciprocating mechanism includes a suspension member rotatably connected to a rear end of the main shaft, a linear bearing that holds the suspension member so as to be movable up and down, and the suspension member. A suspension member clamping device that clamps or unclamps the bearing to a linear bearing, a crank mechanism connected to the suspension member, a crank pin mounting member that adjusts an eccentric amount of the crank mechanism, and a drive motor that drives the crank mechanism Provided. The suspension member moved up and down by the crankshaft can be fixed by the suspension member clamping device. Thus, the clutch is engaged (turned on / off).
本発明の主軸駆動装置においては、軸方向長さが長くとれるので、剛性の高く、精度の高い主軸を提供するものとなった。高速回転時は転がり軸受で支持され、割出し時は、滑り軸受により支持される。クラッチの接続又は切断は軸方向へ移動するだけでよく機構が簡単、確実である。なお、静圧軸受にすればより精度の高い加工が可能である。 In the spindle drive device of the present invention, since the axial length can be increased, a spindle having high rigidity and high accuracy is provided. It is supported by a rolling bearing during high-speed rotation, and is supported by a sliding bearing during indexing. The clutch can be connected or disconnected only by moving in the axial direction, and the mechanism is simple and reliable. If a hydrostatic bearing is used, processing with higher accuracy is possible.
さらに、請求項２に記載の発明においては、滑り軸受により軸方向に移動できるので、クラッチの入り切りのみでなく、往復動作もでき、ＮＣ工作機械にように主軸台を往復動させることなく、従来のギヤシェーパと同様な加工機械で穴加工とギヤシェーパの加工を行え、精度の高い歯車を製作できるものとなった。また、往復移動機構により、ギヤシェーパ歯車加工と、穴加工等の旋削を選択するクラッチを操作できるので構造が複雑化することない。 Furthermore, in the invention according to claim 2, since it can be moved in the axial direction by a sliding bearing, it can be reciprocated as well as on / off of the clutch, and without reciprocating the headstock as in an NC machine tool, With the same processing machine as the previous gear shaper, hole drilling and gear shaper processing can be performed, and high-precision gears can be manufactured. In addition, since the reciprocating mechanism can operate a clutch for selecting gear shaper gear machining and turning such as drilling, the structure is not complicated.
また、請求項３に記載の発明においては、割出回転時は割出用駆動モータを用い、穴加工等では高速回転用モータを用いて加工条件にあった速度・精度を得られるので、加工精度が向上し、生産効率も向上する。また、請求項４に記載の発明においては、従動歯車をバックラッシ調整装置に接続できるので、バックラッシのない精度の高い割出加工ができる。 Further, in the invention according to claim 3, since an indexing drive motor is used during indexing rotation, and a high speed rotation motor is used for drilling or the like, the speed and accuracy suitable for the processing conditions can be obtained. Accuracy is improved and production efficiency is improved. In the invention according to claim 4, since the driven gear can be connected to the backlash adjusting device, indexing with high accuracy without backlash can be performed.
さらに、請求項５に記載の発明においては、クランク軸で上下される懸架部材を懸架部材クランプ装置により固定することができるので、クランク機構での位置合わせした後、懸架部材を固定することにより主軸を任意の位置で固定できる。往復運転時には、懸架部材クランプ装置はアンクランプとする。なお、本発明の主軸駆動は、ギヤシェーパに限定されることなく、他の工作機械の工具主軸やワークテーブル等にも適用でき、さらに一般の工作機械をはじめとし、複合工作機械にも有用である。 Furthermore, in the invention described in claim 5, since the suspension member that is moved up and down by the crankshaft can be fixed by the suspension member clamping device, the main shaft can be fixed by fixing the suspension member after the alignment by the crank mechanism. Can be fixed at any position. During the reciprocating operation, the suspension member clamping device is unclamped. The spindle drive according to the present invention is not limited to the gear shaper, but can be applied to a tool spindle or a work table of other machine tools, and is also useful for complex machine tools including general machine tools. .
本発明の実施の形態の主軸駆動装置について説明する。図１に示すように、主軸駆動装置３０は、主軸台３１に転がり軸受３２で支持された中空高速軸３３、中空高速軸内両端から突出しかつ中空高速軸内を滑り軸受３４で回転かつ軸方向に摺動可能に挿通され先端２ａに図示しない工具（ピニオンカッタ等）を取付け可能にされた主軸２を有する。さらに、主軸の後端側に従動平歯車１８が設けられており、従動平歯車の回転により主軸２が回転する。従動平歯車は主軸とは軸方向に摺動可能にかつ主軸と一体に回転し、軸受ブッシュ１８ａと転がり軸受３８で回転自在に支持されている。従動平歯車１８は後述するバックラッシ調整装置１に設けられた割出用モータ８により割出が可能にされている。中空高速軸３３は高速回転用モータ６０に接続されている。また、中空高速軸の軸端に設けられ主軸の軸方向移動に伴って中空高速軸と主軸とを回転方向に切断又は接続可能とするクラッチ３７が設けられている。さらに、主軸２の軸方向の往復動又はクラッチ３７の断続ができるように主軸を軸方向に往復動させる往復移動機構４４を有する。 A spindle driving device according to an embodiment of the present invention will be described. As shown in FIG. 1, the spindle drive device 30 includes a hollow high-speed shaft 33 supported by a spindle head 31 with rolling bearings 32, projects from both ends of the hollow high-speed shaft, and rotates in the hollow high-speed shaft with a slide bearing 34 and is axially driven. The main shaft 2 is slidably inserted into the tip 2a, and a tool (such as a pinion cutter) (not shown) can be attached to the tip 2a. Further, a driven spur gear 18 is provided on the rear end side of the main shaft, and the main shaft 2 is rotated by the rotation of the driven spur gear. The driven spur gear is slidable in the axial direction with respect to the main shaft and rotates integrally with the main shaft, and is rotatably supported by the bearing bush 18a and the rolling bearing 38. The driven spur gear 18 can be indexed by an indexing motor 8 provided in the backlash adjusting device 1 described later. The hollow high speed shaft 33 is connected to a motor 60 for high speed rotation. In addition, a clutch 37 is provided at the shaft end of the hollow high-speed shaft so that the hollow high-speed shaft and the main shaft can be disconnected or connected in the rotational direction as the main shaft moves in the axial direction. Furthermore, a reciprocating mechanism 44 for reciprocating the main shaft in the axial direction is provided so that the main shaft 2 can be reciprocated in the axial direction or the clutch 37 can be engaged and disengaged.
詳述すると、図１、２、４に示すように、中空高速軸３３は主軸台３１に転がり軸受３２・・３２で支持され、主軸２（回転軸）は、中空高速軸内３３ｂに滑り軸受３４を介して回転かつ軸方向に摺動自在に挿通されている。主軸２の両端は中空高速軸内から突出し、先端２ａには工具取付穴３５、ドローバ穴３６が開けられ、工具着脱機構（クランプユニット３６ａ及びドローバ３６ｂ）により図示しない工具が取付け、取り外し可能にされている。 More specifically, as shown in FIGS. 1, 2, and 4, the hollow high-speed shaft 33 is supported on the headstock 31 by rolling bearings 32 and 32, and the main shaft 2 (rotating shaft) is a sliding bearing in the hollow high-speed shaft 33b. It is inserted through 34 so as to be rotatable and slidable in the axial direction. Both ends of the main shaft 2 protrude from the hollow high-speed shaft, a tool mounting hole 35 and a draw bar hole 36 are opened at the tip 2a, and a tool (not shown) can be attached and detached by a tool attaching / detaching mechanism (clamp unit 36a and draw bar 36b). ing.
また、中空高速軸３３の先端には切り欠き３３ａが設けられ、主軸２の先端側外周には、キー２ｄが設けられている。主軸を軸方向に移動させ、このキーを切り欠き３３ａに嵌合又は離脱することによりクラッチ３７を構成し、主軸と中空高速軸３３を一体に回転、又は分離できる。図２は中空高速軸と主軸とがかみ合った状態を示し、図３は分離した状態を示している。主軸を図で見て下方に移動させると切り欠き３３ａからキー２ｄが離れ、クラッチが切断される。中空高速軸の切り欠き３３ａに続いてプーリ４１が設けられている。高速回転用モータ６０が中間高速軸３３と平行の出力軸６０ｃを下側に向けて主軸台３１に取付けられている。プーリベルト４２、プーリ４１を介して中空高速軸が高速回転用モータにより回転可能に接続されている。 Further, a notch 33 a is provided at the tip of the hollow high-speed shaft 33, and a key 2 d is provided on the tip side outer periphery of the main shaft 2. By moving the main shaft in the axial direction and fitting or disengaging this key from the notch 33a, the clutch 37 is formed, and the main shaft and the hollow high-speed shaft 33 can be rotated or separated together. FIG. 2 shows a state where the hollow high-speed shaft and the main shaft are engaged with each other, and FIG. 3 shows a separated state. When the spindle is moved downward as seen in the figure, the key 2d is released from the notch 33a, and the clutch is disconnected. A pulley 41 is provided following the notch 33a of the hollow high-speed shaft. A motor 60 for high speed rotation is attached to the head stock 31 with an output shaft 60c parallel to the intermediate high speed shaft 33 facing downward. A hollow high-speed shaft is rotatably connected by a high-speed rotation motor via a pulley belt 42 and a pulley 41.
中空高速軸３３の後端側には、逃げ穴３３ｃ、軸受ブッシュ穴３３ｄ、止めブッシュ穴３３ｅが順次設けられている。中空高速軸３３の軸受ブッシュ穴３３ｄに軸受ブッシュ１８ａが嵌挿され、軸受ブッシュ鍔部１８ｂの先端側端面が軸受ブッシュ穴と止めブッシュ挿入穴３３ｅの段差に当接するようにされている。軸受ブッシュ鍔部１８ｂの後端側端面に隙間をもって当接するように止めブッシュ３３ｆが止めブッシュ穴３３ｅに挿入され、中空高速軸端面３３ｇにねじ固定されている。これにより、軸受ブッシュ１８ａは中空高速軸に対して回転自在にされている。 On the rear end side of the hollow high-speed shaft 33, a clearance hole 33c, a bearing bush hole 33d, and a stop bush hole 33e are sequentially provided. The bearing bush 18a is fitted into the bearing bush hole 33d of the hollow high-speed shaft 33, and the end surface on the front end side of the bearing bush flange 18b is in contact with the step between the bearing bush hole and the stop bush insertion hole 33e. A stop bush 33f is inserted into the stop bush hole 33e so as to abut on the rear end side end surface of the bearing bush flange 18b with a gap, and is screwed to the hollow high-speed shaft end surface 33g. As a result, the bearing bush 18a is rotatable with respect to the hollow high-speed shaft.
さらに、軸受ブッシュ１８ａは十字スプライン穴１８ｃを有する鍔付き補強部材１８ｅに嵌着されている。鍔付き補強部材１８ｅの鍔１８ｆ端に従動平歯車１８がねじ固定されている。また、従動平歯車は反軸受ブッシュ１８ａ側で上部転がり軸受３８を介して主軸台３１に支持されている。これにより、従動平歯車１８は、軸受ブッシュ１８ａを介して中空高速軸３３内を回転自在に支持される。 Further, the bearing bush 18a is fitted to a flanged reinforcing member 18e having a cross spline hole 18c. The driven spur gear 18 is screwed to the end of the flange 18f of the flanged reinforcing member 18e. The driven spur gear is supported on the head stock 31 via the upper rolling bearing 38 on the side opposite to the bearing bush 18a. As a result, the driven spur gear 18 is rotatably supported in the hollow high-speed shaft 33 via the bearing bush 18a.
主軸２の後端側には、前述した軸受ブッシュ１８ａの十字スプライン穴１８ｃにキー嵌合する十字形状のキー２ｂを有する（キー）スプラインブッシュ２ｃが嵌合固定されている。このスプラインブッシュ２ｃが軸受ブッシュ１８ａに嵌合されており、主軸と従動平歯車１８とを軸方向移動自在に一体に回転させる。これにより、割出モータ８の回転が従動平歯車１８を介して主軸２に伝達される。さらに、図１、５に示すように、主軸２はラジアル軸受及びスラスト軸受を組み合わせた回転自在に軸方向接続できる回転継手４３を介して、往復移動装置４４に接続されている。これにより、従動平歯車１８及び主軸２が中空高速軸内３３ｂを回転自在にされる。なお、回転継ぎ手４３は球面軸受等でもよいことはいうまでもない。 On the rear end side of the main shaft 2, a (key) spline bush 2c having a cross-shaped key 2b that is key-fitted into the above-described cross spline hole 18c of the bearing bush 18a is fitted and fixed. The spline bush 2c is fitted to the bearing bush 18a, and rotates the main shaft and the driven spur gear 18 so as to be movable in the axial direction. Thereby, the rotation of the indexing motor 8 is transmitted to the main shaft 2 via the driven spur gear 18. Further, as shown in FIGS. 1 and 5, the main shaft 2 is connected to a reciprocating device 44 through a rotary joint 43 that can be axially connected in a rotatable manner by combining a radial bearing and a thrust bearing. As a result, the driven spur gear 18 and the main shaft 2 are rotatable in the hollow high-speed shaft 33b. Needless to say, the rotary joint 43 may be a spherical bearing or the like.
図１、５に示すように、往復移動装置４４は略して示す回転継手４３に接続された懸架部材４５をリニアガイド４６に沿って上下方向に移動させる。即ち、主軸２をリニアガイド４６に沿って上下方向に移動させる。懸架部材４５は移動クランプ４７の進退により、懸架部材の位置を固定（クランプ）又は上下移動可能（アンクランプ）にされる。即ち、移動クランプ４７により、主軸２の位置固定と軸方向移動との選択が可能となる。懸架部材４５には工具着脱用シリンダ４８が内蔵され、前述したドローバ３６ｂを上下させて工具を着脱する。懸架部材４５の上端には懸架部材の移動方向と直角方向にスライダ溝４９が設けられている。 As shown in FIGS. 1 and 5, the reciprocating device 44 moves the suspension member 45 connected to the rotary joint 43, which is abbreviated, in the vertical direction along the linear guide 46. That is, the main shaft 2 is moved in the vertical direction along the linear guide 46. The suspension member 45 is fixed (clamped) or vertically movable (unclamped) by moving the moving clamp 47 forward and backward. That is, the moving clamp 47 enables selection between the position fixing of the main shaft 2 and the movement in the axial direction. The suspension member 45 incorporates a tool attaching / detaching cylinder 48, and the above-described draw bar 36b is moved up and down to attach and detach the tool. A slider groove 49 is provided at the upper end of the suspension member 45 in a direction perpendicular to the moving direction of the suspension member.
スライダ溝４９にクランクピン５０先端が嵌合されている。さらに、クランクピン５０はクランプピン取付部材５１を介して回転板５２に偏心可能に取付けられている。回転板の回転によりクランクピンを介してスライダ溝を上下させクランク機構を構成し、懸架部材４５を上下移動させる。さらに、懸架部材、回転継手４３を介して主軸２が上下運動する。回転板５２は歯車減速機構５４を介して上下用モータ５５により回転される。 The front end of the crank pin 50 is fitted in the slider groove 49. Further, the crank pin 50 is attached to the rotating plate 52 via a clamp pin attaching member 51 so as to be eccentric. By rotating the rotating plate, the slider groove is moved up and down via the crank pin to constitute a crank mechanism, and the suspension member 45 is moved up and down. Further, the main shaft 2 moves up and down via the suspension member and the rotary joint 43. The rotating plate 52 is rotated by a vertical motor 55 via a gear reduction mechanism 54.
回転板５２の軸直角方向に送りねじ５６が設けられ、クランプピン取付部材５１が送りねじに螺合されている。送りねじ５６の回転によりクランプピン取付部材５１を軸直角方向に移動させ、クランクピン５０の偏心量を調整する。送りねじ５６の端面には、六角穴５６ａが設けられており、この六角穴に嵌合可能なナットランナ５７が進退可能かつ回転可能に設けられている。ナットランナ５７はランナシリンダ５８により進退され、位置決めモータ５９により回転可能にされている。クランプピン取付部材５１はクランプシリンダ５３の進退により位置保持（クランプ）又は移動可能（アンクランプ）にされる。 A feed screw 56 is provided in the direction perpendicular to the axis of the rotary plate 52, and the clamp pin mounting member 51 is screwed to the feed screw. The clamp pin mounting member 51 is moved in the direction perpendicular to the axis by the rotation of the feed screw 56, and the eccentric amount of the crank pin 50 is adjusted. A hexagonal hole 56a is provided on the end face of the feed screw 56, and a nut runner 57 that can be fitted into the hexagonal hole is provided so as to be movable forward and backward. The nut runner 57 is advanced and retracted by a runner cylinder 58 and is rotated by a positioning motor 59. The clamp pin mounting member 51 is held (clamped) or movable (unclamped) by moving the clamp cylinder 53 back and forth.
クランクピン５０の位置決めは次のように行う。クランプシリンダ５３を後退させクランプピン取付部材５１のクランプを解除する。位置決めモータ５９を回転させながら空気圧式のランナシリンダ５８を進めてナットランナを六角穴に差し込みながら、さらに位置決めモータ５９を回転させ、クランプピン取付部材（クランクピン）が所望の位置になるように調整する。調整が完了したら、クランプシリンダ５３を前進させクランプピン取付部材５１を固定する。次にランナシリンダ５８を後退させ、ナットランナを六角穴から外し、原位置に戻す。なお、ナットランナと六角穴の位相をあわせてから回転させて位置決めしてもよい。 The crank pin 50 is positioned as follows. The clamp cylinder 53 is moved backward to release the clamp of the clamp pin mounting member 51. While the positioning motor 59 is rotated, the pneumatic runner cylinder 58 is advanced to insert the nut runner into the hexagonal hole, and the positioning motor 59 is further rotated to adjust the clamp pin mounting member (crank pin) to a desired position. . When the adjustment is completed, the clamp cylinder 53 is advanced and the clamp pin mounting member 51 is fixed. Next, the runner cylinder 58 is retracted, and the nut runner is removed from the hexagonal hole and returned to the original position. In addition, you may rotate and position after adjusting a nut runner and the phase of a hexagon socket.
図１、２及び図４乃至図６に示すように、主軸台３１にはさらに、主軸２の従動平歯車のバックラッシを調整するとともに、駆動するバックラッシ調整装置１が取付けられている。図に示すように、バックラッシ調整装置１は従動平歯車１８の側面に設けられ、バックラッシ調整装置の端部に割出用駆動モータ８が設けられている。割出用駆動モータ８は回転割出精度が高いサーボモータが用いられ、遊星減速機９を介して減速され、出力軸１０を介して左ねじれの駆動はすば歯車１１に接続されている。図６に示すように、左ねじれの駆動はすば歯車１１の両側にはそれぞれ、右ねじれの第１及び第２のはすば歯車１２、１５がかみ合うようにされている。この第１及び第２のはすば歯車１２、１５は、それぞれ第１及び第２の中間軸２１、２２の下方側に設けられている。第１及び第２の中間軸の上方側にそれぞれ第１及び第２の平歯車１３、１６が設けられ、第１及び第２の平歯車とかみ合う第１及び第２の中間平歯車１４、１７が順次設けられている。この第１及び第２の中間平歯車１４、１７は、主軸２の従動平歯車１８を二カ所から同時にかみ合うようにされている。 As shown in FIGS. 1, 2 and 4 to 6, a backlash adjusting device 1 that drives and drives the backlash of the driven spur gear of the main shaft 2 is further attached to the headstock 31. As shown in the figure, the backlash adjusting device 1 is provided on the side surface of the driven spur gear 18, and an indexing drive motor 8 is provided at the end of the backlash adjusting device. The indexing drive motor 8 is a servomotor with high rotational indexing accuracy, decelerated via a planetary speed reducer 9, and the left-twisted drive is connected to a helical gear 11 via an output shaft 10. As shown in FIG. 6, the right-handed first and second helical gears 12 and 15 are engaged with both sides of the helical gear 11 as shown in FIG. The first and second helical gears 12 and 15 are provided below the first and second intermediate shafts 21 and 22, respectively. First and second spur gears 13 and 16 are respectively provided on the upper side of the first and second intermediate shafts, and the first and second intermediate spur gears 14 and 17 mesh with the first and second spur gears. Are provided sequentially. The first and second intermediate spur gears 14 and 17 are configured to simultaneously mesh the driven spur gear 18 of the main shaft 2 from two places.
第１及び第２の中間軸２１，２２は、それぞれ油圧作動のバックラッシ調整シリンダ２４、２５により軸方向に移動し、はすば歯車のかみ合い状態を押し合い状態にしてバックラッシを調整するようにされている。例えば、第１（又は第２）の中間軸を図６で見て下方向へ移動すると第１（又は第２）のはすば歯車１４は右回転方向に力を受ける。同時に駆動はすば歯車１１は左回転方向に力を受け、従動平歯車１８の歯面を互いに反対側に押すようにしてバックラッシを無くすあるいは少なくすることができる。中間軸２１、２２を互いに逆方向に移動させると少ない移動量でかみ合い量を増して歯車列の隙間は少なくなりさらには歯車面同士が圧接される。これにより、サーボモータ８による主軸２のバックラッシなしの高精度の割出を行うことができる。 The first and second intermediate shafts 21 and 22 are moved in the axial direction by hydraulically operated backlash adjusting cylinders 24 and 25, respectively, to adjust the backlash by pushing the meshing state of the helical gear. Yes. For example, when the first (or second) intermediate shaft is moved downward as viewed in FIG. 6, the first (or second) helical gear 14 receives a force in the clockwise direction. At the same time, the driving helical gear 11 receives a force in the counterclockwise direction and pushes the tooth surfaces of the driven spur gear 18 to the opposite sides to eliminate or reduce backlash. When the intermediate shafts 21 and 22 are moved in directions opposite to each other, the meshing amount is increased with a small amount of movement, the gap between the gear trains is reduced, and the gear surfaces are pressed against each other. As a result, high-precision indexing without backlash of the spindle 2 by the servo motor 8 can be performed.
さらに、第１及び第２の中間平歯車１４、１７はそれぞれ油圧作動のシフトシリンダ２６、２７により軸方向に移動し、従動平歯車１８とかみ合い又はかみ合いを解除できるようにされている。シフトシリンダをシフトさせかみ合いを外せば、主軸２とバックラッシ調整装置１とが切り離される。サーボモータ８、バックラッシ調整シリンダ１４、１７、シフトシリンダ２６、２７はそれぞれ異なる歯車軸に設けられているので、構造が簡単であり、軸方向の大きさも小さくできる。 Further, the first and second intermediate spur gears 14 and 17 are moved in the axial direction by hydraulically operated shift cylinders 26 and 27, respectively, so as to be able to engage with or release the driven spur gear 18. When the shift cylinder is shifted to disengage the main shaft 2 and the backlash adjusting device 1 are separated. Since the servo motor 8, the backlash adjusting cylinders 14 and 17, and the shift cylinders 26 and 27 are provided on different gear shafts, the structure is simple and the size in the axial direction can be reduced.
かかる構成の主軸駆動装置３０において、作動について一例を説明する。高速回転時には、まず、クラッチ３７の位置を合わせる。次に図１、図５に示すように、上下用モータ５５を回転させ、回転板５２の送りねじ５６が主軸２と同方向となるような位置にする。そして、クランプピン取付部材５１の位置を調整できるようにし、位置決めモータ５９を回転させ、クランプピン取付部材５１を上方に移動、即ち主軸２を上方に移動させ、図１、２に示すように、主軸２のキー２ｄと中空高速軸３３の切り欠き３３ａを嵌合し一体にする。さらに、移動クランプ４７を進め懸架部材４５の位置を固定（クランプ）する。これにより、主軸２と中空高速軸３３とは一体となる。 An example of the operation of the spindle driving device 30 having such a configuration will be described. At the time of high speed rotation, first, the position of the clutch 37 is adjusted. Next, as shown in FIGS. 1 and 5, the vertical motor 55 is rotated so that the feed screw 56 of the rotating plate 52 is in the same direction as the main shaft 2. Then, the position of the clamp pin mounting member 51 can be adjusted, the positioning motor 59 is rotated, the clamp pin mounting member 51 is moved upward, that is, the main shaft 2 is moved upward, as shown in FIGS. The key 2d of the main shaft 2 and the notch 33a of the hollow high-speed shaft 33 are fitted and integrated. Further, the moving clamp 47 is advanced to fix (clamp) the position of the suspension member 45. Thereby, the main shaft 2 and the hollow high-speed shaft 33 are integrated.
一方、図２のバックラッシ調整装置１のバックラッシ調整シリンダ２４、２５を軸方向に移動し、バックラッシを与える。次に図４に示すように、シフトシリンダ２６、２７を進め、第１及び第２の中間平歯車１４、１７を従動平歯車１８からかみ合いを解除する。高速回転用モータ６０を回転させ、プーリベルト４２、プーリを介して中空高速軸３３、主軸２、従動平歯車１８を回転させる。なお、クランプピン取付部材５１の位置は、クランク動作させる場合の範囲にクラッチ３７の断続に必要な距離をプラスした値より外側である。なお、クランクピンを移動させてクラッチ３７の断続（入切）を行った例を示したが、単純に往復移動機構４４全体を上下に移動させるようにして、クラッチの断続を行うようにしてもよい。 On the other hand, the backlash adjusting cylinders 24 and 25 of the backlash adjusting device 1 of FIG. 2 are moved in the axial direction to give backlash. Next, as shown in FIG. 4, the shift cylinders 26 and 27 are advanced to disengage the first and second intermediate spur gears 14 and 17 from the driven spur gear 18. The motor 60 for high speed rotation is rotated, and the hollow high speed shaft 33, the main shaft 2, and the driven spur gear 18 are rotated through the pulley belt 42 and the pulley. Note that the position of the clamp pin mounting member 51 is outside a value obtained by adding a distance necessary for the engagement / disengagement of the clutch 37 to the range in which the crank operation is performed. Although the example in which the crank pin is moved to engage / disengage the clutch 37 has been shown, the entire reciprocating mechanism 44 may be moved up and down to engage / disengage the clutch. Good.
割出回転時には、まず、移動クランプ４７を後退させ懸架部材４５を移動できる（アンクランプ）ようにする。次に、クランプピン取付部材５１の位置を調整できるようにし、位置決めモータ５９を回転させ、クランプピン取付部材５１を移動し、主軸の移動が所定の往復動作範囲となるように設定し、クランプシリンダ５３を前進させクランプピン取付部材５１位置を固定する。このとき、図３に示すように、クラッチ３７は解除され、主軸２と中空高速軸３３は互いに回転自在となる。 At the time of indexing rotation, first, the moving clamp 47 is moved backward so that the suspension member 45 can be moved (unclamped). Next, the position of the clamp pin mounting member 51 can be adjusted, the positioning motor 59 is rotated, the clamp pin mounting member 51 is moved, the movement of the main shaft is set so as to be within a predetermined reciprocating operation range, and the clamp cylinder 53 is advanced to fix the clamp pin mounting member 51 position. At this time, as shown in FIG. 3, the clutch 37 is released, and the main shaft 2 and the hollow high-speed shaft 33 are rotatable with respect to each other.
一方、図１、２、５に示すように、バックラッシ調整装置１のシフトシリンダ２６、２７を後退させ、第１及び第２の中間平歯車１４、１７と従動平歯車１８をかみ合わせる。バックラッシ調整シリンダ２４、２５を軸方向に移動させバックラッシを無くす。次に、割出用駆動モータ８を回転させ、バックラッシ調整装置を介して従動平歯車を回転させ、バックラッシのない回転を主軸２に与える。同時に上下用モータ５５を回転させて主軸を上下方向に往復動させる。これにより、例えば、ギヤシェーパ加工が可能となる。 On the other hand, as shown in FIGS. 1, 2, and 5, the shift cylinders 26 and 27 of the backlash adjusting device 1 are moved backward to engage the first and second intermediate spur gears 14 and 17 and the driven spur gear 18. The backlash adjustment cylinders 24 and 25 are moved in the axial direction to eliminate backlash. Next, the indexing drive motor 8 is rotated, the driven spur gear is rotated via the backlash adjusting device, and rotation without backlash is applied to the main shaft 2. At the same time, the vertical motor 55 is rotated to reciprocate the main shaft in the vertical direction. Thereby, for example, gear shaper processing becomes possible.
以上のように、本発明の実施の形態においては、バックラッシ調整装置の割出用駆動モータ８と従動平歯車１８とを切断、接続可能とした。また、高速回転用モータ６０に接続された中空高速軸３３内を軸方向に移動かつ回転可能にされた主軸２の先端に工具を取付けるようにした。これにより、ギヤシェーパのような往復、割出加工を行えると共に、高速回転による穴や筒等の旋削加工ができる複合工作機械を提供するものとなった。 As described above, in the embodiment of the present invention, the indexing drive motor 8 and the driven spur gear 18 of the backlash adjusting device can be disconnected and connected. Further, the tool is attached to the tip of the main shaft 2 that is movable and rotatable in the axial direction in the hollow high-speed shaft 33 connected to the high-speed rotation motor 60. As a result, it has become possible to provide a composite machine tool that can perform reciprocating and indexing work like a gear shaper and can turn holes and cylinders by high-speed rotation.
割出加工時には、バックラッシがなく、割出精度よく行われる。この場合、高速用モータ(スピンドルモータ)６０は回転しないのでトルク損失や振動も少ない。また、高速回転動作においては、割出用モータ８を有するバックラッシ調整装置１と従動平歯車１８との噛み合いは解除されるので、振動やトルク損失の影響も少なく、スムースな回転が可能である。 When indexing, there is no backlash and the indexing is performed with high accuracy. In this case, since the high speed motor (spindle motor) 60 does not rotate, there is little torque loss and vibration. Further, in the high-speed rotation operation, the meshing between the backlash adjusting device 1 having the indexing motor 8 and the driven spur gear 18 is released, so that smooth rotation is possible with less influence of vibration and torque loss.
なお、上部転がり軸受３８を挟んで従動平歯車１８の上部に環状のカバー３９がねじ固定されている。カバー３９の下側には環状のオイルパン４０が設けられ、外部からの塵埃の侵入を防ぐ。従動平歯車１８、カバー３９には、鍔付き補強部材１８ｅと同形状、同位相に十字スプライン穴１８ｃが設けられている。また、十字スプライン穴１８ｃは、十字に限らず、対向する一組のキー穴、多数の歯を有するスプライン穴等、回転を伝達し、軸方向に移動可能な軸嵌合機構であればよい。さらに、図４に示す符号６１は、主軸２のみを作動させる時に、中空高速軸３３を固定するクランプである。符号６２はクランプ３７のクランプ位置を割り出すための位置決め用クランプ、符号６３は中空高速軸内の軸受３４に潤滑剤を供給するために中空高速軸外周面に着脱可能にされた給油口及び排油口である。また、各制御はＮＣ制御等種々の制御により制御される。また、例として図３の符号６４で示す検出器等は各図に示すように適宜設定されることはいうまでもない。 An annular cover 39 is screwed to the upper portion of the driven spur gear 18 with the upper rolling bearing 38 interposed therebetween. An annular oil pan 40 is provided below the cover 39 to prevent dust from entering from the outside. The driven spur gear 18 and the cover 39 are provided with a cross spline hole 18c in the same shape and phase as the flanged reinforcing member 18e. The cross spline hole 18c is not limited to a cross, and may be any shaft fitting mechanism that transmits rotation and moves in the axial direction, such as a pair of opposing key holes and a spline hole having a large number of teeth. Further, reference numeral 61 shown in FIG. 4 is a clamp for fixing the hollow high-speed shaft 33 when only the main shaft 2 is operated. Reference numeral 62 denotes a positioning clamp for determining the clamp position of the clamp 37, and reference numeral 63 denotes an oil supply port and an oil drain which are detachably attached to the outer peripheral surface of the hollow high speed shaft in order to supply a lubricant to the bearing 34 in the hollow high speed shaft. The mouth. Each control is controlled by various controls such as NC control. Further, as an example, it goes without saying that the detector indicated by the reference numeral 64 in FIG. 3 is appropriately set as shown in each figure.
以上本発明の実施の形態について、述べたが、本実施の形態に限らず適宜適用が可能であることはいうまでもない。また、バックラッシ調整装置は本発明の実施の形態に限らず他の形態のものであってもよい。バックラッシが問題とならなければ、バックラッシ調整装置を介さず単に割出用駆動モータと接続してもよい。また、往復移動装置は特許文献１のような従来のものに、クラッチ３７の断続（入切）のできる上下機構を付加する等、適宜適用できることはいうまでもない。 Although the embodiment of the present invention has been described above, it is needless to say that the present invention is not limited to this embodiment and can be appropriately applied. Further, the backlash adjusting device is not limited to the embodiment of the present invention, but may be of another form. If backlash does not matter, it may be simply connected to the indexing drive motor without going through the backlash adjusting device. Needless to say, the reciprocating device can be appropriately applied to a conventional device such as Patent Document 1 by adding an up-and-down mechanism capable of connecting / disconnecting the clutch 37.
１ バックラッシ調整装置。
２ 回転軸（主軸）
２ａ 主軸先端
２ｂ 主軸の後端
８ 割出用駆動モータ
１８ 従動平歯車
３０ 主軸駆動装置
３１ 主軸台
３２ 転がり軸受
３３ 中空高速軸
３３ｂ 中空高速軸内
３４ 滑り軸受
３７ クラッチ
４４ 往復移動機構
４５ 懸架部材
４６ リニア軸受
４７ 懸架部材クランプ装置
５１ クランクピン取付部材
５４ クランク機構
５５ 駆動モータ
６０ 高速回転用モータ
1 Backlash adjustment device.
2 Rotating shaft (spindle)
2a Main shaft tip 2b Main shaft rear end 8 Indexing drive motor 18 Driven spur gear 30 Main shaft drive device 31 Main shaft base 32 Rolling bearing 33 Hollow high speed shaft 33b Hollow high speed shaft 34 Sliding bearing 37 Clutch 44 Reciprocating mechanism 45 Suspension member 46 Linear bearing 47 Suspension member clamping device 51 Crank pin mounting member 54 Crank mechanism 55 Drive motor 60 Motor for high speed rotation
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| JP2011057875A JP5741909B2 (en) | 2011-03-16 | 2011-03-16 | Spindle drive |
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| JP2011057875A JP5741909B2 (en) | 2011-03-16 | 2011-03-16 | Spindle drive |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103231088A (en) * | 2013-05-13 | 2013-08-07 | 佛山市圣特斯数控设备有限公司 | Multi-station turntable type special drilling machine |
| CN104439380A (en) * | 2014-12-09 | 2015-03-25 | 重庆市旺成科技股份有限公司 | Machine tool for drilling motorcycle clutch central sleeve oil hole |
| CN105598775A (en) * | 2015-12-29 | 2016-05-25 | 山西顾德宝丰重工机械有限公司 | Roller carrier shaft burr polishing mechanism and method |
| CN107700078A (en) * | 2017-10-17 | 2018-02-16 | 江苏金龙科技股份有限公司 | The main shaft driving device of needing machine |
| CN108336700A (en) * | 2018-04-17 | 2018-07-27 | 国电联合动力技术有限公司 | A kind of segmented crossing spline penetration pipe axis and the marine tidal-current energy unit including it |
| CN108555619A (en) * | 2018-06-21 | 2018-09-21 | 江苏大学 | A kind of wheel rim double-station positioner device |
| CN111372722A (en) * | 2017-12-22 | 2020-07-03 | 斗山机床株式会社 | Spindle drive device for machine tool |
| CN113043068A (en) * | 2021-02-22 | 2021-06-29 | 宁波海天精工股份有限公司 | Micro-degree indexing mechanism |
| CN114932453A (en) * | 2022-06-28 | 2022-08-23 | 通用技术齐齐哈尔二机床有限责任公司 | Precise indexing mechanism for main shaft of numerical control heavy horizontal machine tool |
Families Citing this family (1)
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| CN105618811A (en) * | 2016-03-10 | 2016-06-01 | 中山市鸿程科研技术服务有限公司 | Vertical drilling mechanism for multifunctional automatic machining integrated machine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103231088A (en) * | 2013-05-13 | 2013-08-07 | 佛山市圣特斯数控设备有限公司 | Multi-station turntable type special drilling machine |
| CN104439380A (en) * | 2014-12-09 | 2015-03-25 | 重庆市旺成科技股份有限公司 | Machine tool for drilling motorcycle clutch central sleeve oil hole |
| CN105598775A (en) * | 2015-12-29 | 2016-05-25 | 山西顾德宝丰重工机械有限公司 | Roller carrier shaft burr polishing mechanism and method |
| CN107700078A (en) * | 2017-10-17 | 2018-02-16 | 江苏金龙科技股份有限公司 | The main shaft driving device of needing machine |
| CN111372722A (en) * | 2017-12-22 | 2020-07-03 | 斗山机床株式会社 | Spindle drive device for machine tool |
| CN108336700A (en) * | 2018-04-17 | 2018-07-27 | 国电联合动力技术有限公司 | A kind of segmented crossing spline penetration pipe axis and the marine tidal-current energy unit including it |
| CN108555619A (en) * | 2018-06-21 | 2018-09-21 | 江苏大学 | A kind of wheel rim double-station positioner device |
| CN108555619B (en) * | 2018-06-21 | 2019-12-03 | 江苏大学 | A kind of wheel rim double-station positioner device |
| CN113043068A (en) * | 2021-02-22 | 2021-06-29 | 宁波海天精工股份有限公司 | Micro-degree indexing mechanism |
| CN114932453A (en) * | 2022-06-28 | 2022-08-23 | 通用技术齐齐哈尔二机床有限责任公司 | Precise indexing mechanism for main shaft of numerical control heavy horizontal machine tool |
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Free format text: JAPANESE INTERMEDIATE CODE: R350 |