JP5741910B2 - Spindle drive using backlash adjusting device - Google Patents

Description

  The present invention relates to a backlash adjusting device for adjusting a backlash of a gear transmission device of a machine tool and a spindle driving device using the backlash adjusting device.

  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. Furthermore, with the progress of multi-task machine tools, in addition to the indexing function on the rotary table for mounting or fixing the workpiece or the tool spindle to which the tool is attached, the number of tools capable of high-speed rotation such as drilling the workpiece has increased. Yes. In such a case, an indexing motor and a high-speed rotation motor are provided, and the main shaft and each motor are selectively connected by a clutch or the like 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.

  A machine tool having such an indexing mechanism requires indexing accuracy. However, since indexing is transmitted from the drive shaft to the tool spindle and the rotary table shaft via a plurality of gears, indexing accuracy is reduced due to backlash by the gears.

  Therefore, in FIG. 1 of Patent Document 3, although for table rotation, a backlash adjusting device 81 as shown in FIG. 6 is used to reduce backlash. 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. 6 shows the high-speed rotation.

  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.

  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. 6, 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.

  However, in such a conventional one, the moving second or fourth helical gears 94 and 97 and the driven helical gear 18 move in the axial direction and the tooth surfaces contact each other in the tooth width direction. Since a non-contact portion occurs, uneven wear and vibration may occur.

  Therefore, in the turning table 2 of FIG. 4 of Patent Document 4, as shown in FIG. 7, the drive shaft 87 is moved without moving the first and second intermediate shafts 85 and 86. In the backlash adjusting device 81 of Patent Document 3, a set of helical drive gears 91 and 93 having a reverse twisting direction are provided on the drive shaft 87, and the lower drive meshes with the helical gear 91 as seen in the figure. The helical gear 92 and the first helical gear coaxially with the first helical gear include a second helical gear 94 whose helical direction is opposite (reverse twist). The first intermediate shaft 85 is provided.

  In addition to the first helical gear 92, as shown in the figure, a third helical gear 95 that meshes with the helical gear 93 on the upper drive side, and a third helical gear 95 that is coaxial with the third helical gear. The third helical gear is provided as a second intermediate shaft 86 by providing a fourth helical gear 97 having the same helical direction. 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. A drive gear 98 is provided on the drive shaft 87 so as to mesh with the gear 99 of the output shaft 90 of the drive motor 8. The backlash between the driven helical gear 18 and the drive gear 98 is adjusted by moving the drive shaft 87 in the axial direction.

JP-A-10-109223 Japanese Patent No. 2631416 JP 2001-246533 A JP-A-8-197366

  However, in Patent Document 3, since both the high-speed and indexing motor are provided, the structure on the backlash side is complicated. The thing of patent document 4 had the problem that the number of stages of the axial direction of a gearwheel was as many as four stages, even if it provided a high-speed motor separately, and the axial direction height became high. Further, in Patent Document 3, the indexing is performed by the worm gear 102, and in Patent Document 4, the drive motor 8 and the drive shaft 87 are connected by gears 99 and 98, so that the drive motor 8 and the drive shaft 87 are connected. Backlash occurs. For this reason, when the rotation direction of the drive motor is reversed, there is a problem that backlash occurs and indexing accuracy is lowered. Further, in the case of Patent Document 4, if the shift drive shaft 87 and the drive motor shaft 90 are integrated to prevent backlash during reverse rotation, the structure becomes complicated.

  Further, in Patent Document 3, 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 load. And there is a gear resistance. Moreover, in the thing of patent document 4, when another motor was used at the time of high speed rotation, since the gear for backlash swung around, there existed a problem that the load at the time of high speed rotation was large.

  On the other hand, 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 2 were integrated. In addition, in order to apply Patent Document 1 to Patent Document 2, there is a problem that it is necessary to ensure the axial length of the main shaft in order to improve rigidity, and it is necessary to increase the length in the axial direction. There is an example of gear machining similar to a gear shaper by moving a headstock of an NC machine tool in the vertical direction. However, in this case, there is a decrease in speed and accuracy.

  In view of such a problem, an object of the present invention is to provide a small-sized backlash adjusting device that has no backlash even when the drive motor is reversed, has a small number of axial steps, has a simple structure. It is another object of the present invention to provide a spindle drive device that can perform general hole machining and gear shaper machining.

In the present invention, in the drive device for the rotary shaft of the machine tool, the drive helical gear provided on the output shaft of the indexing drive motor and the first helical gear meshing with one of the helical gears. A gear, a first intermediate shaft provided with a first spur gear coaxially with the first helical gear, a first intermediate spur gear meshing with the first spur gear, and the driving helical gear. A second helical gear meshing with the other helical gear, a second intermediate shaft provided with a second spur gear coaxially with the second helical gear, and the second spur gear meshing with each other. A second intermediate spur gear, wherein the first intermediate spur gear and the second intermediate spur gear are simultaneously meshed with a driven spur gear provided on the rotating shaft, and And by moving the second intermediate shaft in the axial direction, the drive is driven between the helical gear and the driven spur gear. A spindle drive with adjustable-Enabled backlash adjusting device Tsu Shi, the rotary shaft includes a hollow high speed shaft supported by the rolling bearing headstock, protruding from the hollow high speed within shaft ends and the A main shaft that is inserted in a hollow high-speed shaft by a sliding 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 other end side, and the main shaft is in the axial direction The driven spur gear is slidable and rotates integrally with the main shaft, and the hollow high-speed shaft is connected to a high-speed rotation motor so that the rotation shaft can be rotated by the high-speed rotation motor. A clutch provided at the shaft end of the hollow high-speed shaft and capable of disconnecting or connecting the hollow high-speed shaft and the main shaft in the rotational direction as the main shaft moves in the axial direction. Axial reciprocation or And solve the problems described above by providing a spindle drive with backlash adjusting device provided with a reciprocating mechanism for reciprocating in the axial direction the spindle to allow intermittent latch.

That is, the axially moving intermediate shaft that adjusts the backlash between the driving helical gear and the driven helical gear is used as the first and second intermediate shafts that mesh on both sides of the driving helical gear, and the axial movement is achieved. The first and second intermediate spur gears that do not move in the axial direction are provided between the first and second spur gears provided on the first and second intermediate shafts and the driven spur gear. Thereby, the backlash can be adjusted by moving the intermediate shaft in the axial direction. Further, even if the meshing point is moved in the axial direction to adjust the backlash, the first and second spur gears do not contact the driven spur gear. Also, the number of gears in the axial direction can be made two. Further, since the main shaft is provided so as to protrude from both ends of the hollow high-speed shaft, the axial length can be increased. During high-speed rotation, the main shaft and the hollow high-speed shaft are coupled by a clutch, and the high-speed rotation motor rotates the hollow high-speed shaft supported by the rolling bearing and the main shaft. 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 an indexing drive motor via a driven gear. Further, 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, and indexing and axial reciprocation can be performed. The reciprocating mechanism doubles as a reciprocating operation at the time of a gear shaper and an operation of a clutch for intermittently connecting the hollow high-speed shaft and the main shaft.

  According to a second aspect of the present invention, the first and second intermediate spur gears are moved by moving one of the first and second intermediate spur gears or the driven spur gear in the axial direction. And the driven spur gear can be disconnected or connected. Thereby, the backlash adjusting device and the driven spur gear can be connected (engaged) or cut off (disengaged). The axial movement distance exceeds the tooth width, and the meshing between the driven spur gear and the intermediate spur gear is engaged with the entire tooth width. Also, make sure there is no meshing when shutting off.

In the spindle drive device using the backlash adjusting device of the present invention, there is no axial movement between the first and second spur gears of the first and second intermediate shafts moving in the axial direction and the driven spur gear. First and second intermediate spur gears were provided. Thus, even when the contact between the first and second spur gears and the first and second intermediate spur gears is not uniform, even if the first intermediate shaft moves in the axial direction, the driven spur gear moves in the axial direction. Since the first and second spur gears do not directly mesh with each other, there is little occurrence of wear or extra unbalanced load due to contact of the meshing point movement. In addition, the drive shaft and the axial movement shaft can be separated, and the structure becomes simple. Moreover, since the number of gears in the axial direction can be two, the height can be reduced and the size can be reduced. In addition, since the axial length can be increased, a high-precision spindle with high rigidity is provided. It is supported by a rolling bearing during high-speed rotation, and is supported by a sliding bearing during indexing and can move in the axial direction. With this, hole machining and gear shaper machining can be performed, and high-precision gears can be manufactured. Further, since the reciprocating mechanism can operate a clutch for selecting gear shaper gear machining and turning such as hole machining, the structure is not complicated. Furthermore, in combination with a motor for high-speed rotation, it can be applied to both high-precision indexing and high-speed rotation processing such as hole and cylindrical processing. Furthermore, if the indexing motor and the backlash adjusting device or the driven gear are separated from each other during high-speed rotation, there will be no accompanying rotation, frictional resistance and load will be reduced, and energy loss will be reduced. The spindle driving device of the present invention is not limited to the gear shaper, but can be applied to other tool spindles, work tables and the like, and is also useful for complex machine tools including general machine tools.

Furthermore, in the invention described in claim 2, since the first and second intermediate spur gears are relatively moved in the axial direction to be connected to or disconnected from the driven spur gear, it is easy to use together with the motor for high speed rotation .

It is a schematic diagram of a backlash adjusting device that constitutes a part of the spindle drive device showing the embodiment of the present invention. It is a fragmentary sectional view of the spindle drive device using the backlash adjusting device which shows embodiment of this invention. It is a fragmentary sectional view which shows the state which disconnected the clutch of the main shaft drive device using the backlash adjusting apparatus which shows embodiment of this invention, and isolate | separated the main shaft and the intermediate rotating shaft. It is a schematic diagram of the main axis | shaft (rotating shaft) of the main-axis drive device using the backlash adjustment apparatus which shows embodiment of this invention. It is a schematic diagram of the driven spur gear side and the reciprocating mechanism of the spindle drive device using the backlash adjusting device showing the embodiment of the present invention. FIG. 6 is a schematic perspective view of a conventional helical gear mechanism. It is a model perspective view of the conventional helical gear mechanism.

Embodiments of the present invention will be described with reference to the drawings. As shown in FIGS. 1 to 4, the backlash adjusting device 1 constituting a part of the spindle driving device 30 of the present invention is used for indexing the spindle 2 to which a tool (not shown) (pinion cutter or the like) is attached at the tip. To do. A driven spur gear 18 is provided on the main shaft, and the main shaft 2 is rotated by the rotation of the driven spur gear.

  The backlash adjusting device 1 is provided on the side surface of the driven spur gear 18. 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 the drawing, the left-handed helical gear 11 is engaged with the right-handed first and second helical gears 12 and 15 on both sides of the helical gear 11, respectively. 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.

  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. 1, 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.

  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.

  Next, the spindle driving device according to the embodiment of the present invention will be described. As shown in FIGS. 2 to 5, the spindle drive device 30 includes a spindle stock 31 to which the backlash adjusting device 1 is attached, a hollow high-speed shaft 33 supported by a rolling bearing 32 on the spindle stock, and projects from both ends of the hollow high-speed shaft. The main shaft 2 is inserted into the hollow high-speed shaft so as to be rotated by the slide bearing 34 and slidable in the axial direction, and a tool can be attached to the tip 2a. Further, a driven spur gear 18 is provided on the other end side of the main shaft. 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 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 turned on and off.

  More specifically, the hollow high-speed shaft 33 is supported on the headstock 31 by rolling bearings 32, 32, and the main shaft 2 (rotating shaft) rotates and slides in the axial direction through the slide bearing 34 in the hollow high-speed shaft 33b. It is inserted freely. 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.

  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 in which the hollow high-speed shaft and the main shaft are engaged with each other. As shown in FIG. 3, when the main shaft is moved downward as seen in the figure, the key 2d is released from the notch 33a, and the clutch is disengaged. 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.

  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.

  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.

  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 FIG. 5, the main shaft 2 is connected to a reciprocating device 44 via a rotary joint 43 such as a spherical bearing that can be axially connected in a rotatable manner. As a result, the driven spur gear 18 and the main shaft 2 are rotatable in the hollow high-speed shaft 33b.

  The reciprocating device 44 moves a suspension member 45 connected to a 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.

  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.

  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.

  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.

  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 FIG. 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, and the clamp pin mounting member 51 is moved upward, that is, the main shaft 2 is moved upward. As shown in FIG. The key 2d 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.

  On the other hand, the backlash adjusting cylinders 24 and 25 of the backlash adjusting device 1 shown in FIGS. 1, 2, and 5 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. Further, although the example in which the crank pin is moved and the clutch 37 is engaged (turned on and off) has been shown, the entire reciprocating mechanism 44 can be moved up and down to engage and disengage the clutch. Good.

  At the time of indexing rotation, first, as shown in FIG. 5, 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, the clutch 37 is released, and the main shaft 2 and the hollow high-speed shaft 33 are rotatable with respect to each other.

  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.

  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.

  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.

  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. Also, as an example, it goes without saying that the detector indicated by reference numeral 64 in FIG. 4 is appropriately set as shown in each figure.

  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 present backlash adjusting device can also be applied to a rotating shaft as in Patent Document 2. 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 Backlash adjustment device.
2 Rotating shaft (spindle)
2a Main shaft tip 8 Indexing drive motor 10 Output shaft 11 Drive helical gear 12 First helical gear 13 First spur gear 14 First intermediate spur gear 15 Second helical gear 16 Second Spur gear 17 Second intermediate spur gear 18 Driven spur gear 21 First intermediate shaft 22 Second intermediate shaft 30 Main shaft drive device 31 Main shaft base 32 Rolling bearing 33 Hollow high-speed shaft 33b Hollow high-speed shaft inside 34 Sliding bearing 37 Clutch 44 reciprocating mechanism 60 motor for high speed rotation

Claims (2)

In a drive device for a rotary shaft of a machine tool, a drive helical gear provided on an output shaft of an indexing drive motor, a first helical gear meshing with one of the helical gears, and the first A first intermediate shaft provided with a first spur gear coaxially with one helical gear, a first intermediate spur gear meshing with the first spur gear, and the drive on the other side of the helical gear. A second helical gear meshing with the second helical gear, a second intermediate shaft provided with a second spur gear coaxially with the second helical gear, and a second intermediate spur gear meshing with the second spur gear. The first intermediate spur gear and the second intermediate spur gear are simultaneously meshed with a driven spur gear provided on the rotating shaft, and further, the first and second intermediate spur gears. By moving the shaft in the axial direction, the backlash between the driving helical gear and the driven spur gear can be adjusted. A spindle drive with backlash adjusting device is, the rotary shaft includes a hollow high speed shaft supported by the rolling bearing headstock, said protruding from the hollow high speed within shaft ends and in the hollow high speed shaft A main shaft that is inserted in a sliding 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 other end side and is slidable in the axial direction with respect to the main shaft; The driven spur gear that rotates integrally with the main shaft, and the hollow high-speed shaft is connected to a high-speed rotation motor so that the rotation shaft can be rotated by the high-speed rotation motor. A reciprocating motion in the axial direction of the main shaft, comprising a clutch provided at a shaft end of the high speed shaft and capable of disconnecting or connecting the hollow high speed shaft and the main shaft in the rotational direction as the main shaft moves in the axial direction Or intermittent clutch Spindle driving device using a reciprocating mechanism for reciprocating the spindle in the axial direction to allow the backlash adjusting device, characterized in that it comprises a. By moving one of the first and second intermediate spur gears or the driven spur gear in the axial direction, the first and second intermediate spur gears and the driven spur gear can be disconnected or connected. A spindle driving device using the backlash adjusting device according to claim 1 .