JPH10109223A - Gear shaver - Google Patents

Abstract

PROBLEM TO BE SOLVED: To facilitate flexible corresponding to various kinds of gear raw materials. SOLUTION: In the case where with the axial reciprocation of a main shaft 19 carried out through a crank mechanism 25, the main shaft 19 is synchronously rotated by synchronization with the rotation of a gear raw material caused by the driving of a Y-axis motor 22 through a command from a control means 30, and at the same time, rotation corresponding to the herical angle of the gear raw material is added to the synchronized rotation to compositely rotate the main shaft 19, and the synchronized rotation with the gear raw material on the main shaft 19 and rotation corresponding to the herical angle are carried out by one Y-axis motor 22 for machining the raw material different in the herical angle, the composite rotation of the main shaft 19 is varied by varying a rotation added to the synchronized rotation for dealing with the raw material, and machining to a plural kinds of gear raw materials can be therefore easily carried out without changing mechanical arrangment to make soft correspondence to many kinds of gear raw materials possible.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear shaper, and is suitable for use in machining a helical gear.

[0002]

2. Description of the Related Art In processing a helical gear in a gear shaper having a tooth profile formed by a pinion cutter, a pinion cutter (cutter) is reciprocated in the axial direction and rotated so as to mesh with a gear material. It needs to be rotated (helical motion).
Conventionally, the helical motion of the cutter is provided by a helical guide mechanism.

A configuration of a conventional gear shaper will be described with reference to FIGS. FIG. 8 shows a schematic configuration of a conventional gear shaper, and FIG. 9 shows a cross section of a main part of the conventional gear shaper.

As shown in the figure, a main shaft 2 on which a pinion cutter (cutter) 1 is mounted is guided via a bearing 3 so as to be reciprocally movable and rotatable in the axial direction. The upper end of the main shaft 2 is connected to the lower end of a connecting rod 5 via a spherical bearing 4,
The connecting rod 5 is connected to a crank mechanism 6. The crank mechanism 6 is rotationally driven by a main shaft motor 6a, and the main shaft 2 is reciprocated in the axial direction via the connecting rod 5 by the rotational driving of the crank mechanism 6. A helical guide male 7 is fixed to the main shaft 2, and the male 7 is supported by a helical guide female 9 fitted to a flange 8. The male shape 7 is guided to the female shape 9 by the axial movement of the main shaft 2, and the main shaft 2 rotates with the axial movement.

A worm wheel 10 is fixed to the flange 8, and a worm (not shown) meshes with the worm wheel 10. By driving a worm (not shown), the main shaft 2 rotates together with the flange 8, the female 9 and the male 7 via the worm wheel 10, and the cutter 1 rotates in synchronization with a gear material (not shown).

That is, the cutter 1 is reciprocated in the axial direction by the rotational drive of the crank mechanism 6, and is rotated by the drive of the worm wheel 10 so as to mesh with the gear material, and at the same time, the male 7 is guided to the female 9. By doing so, it is adapted to be rotated according to the twist angle.

[0007]

However, in the conventional gear shaper, since the angle of one helical guide is fixed, the cutter 1 that can be used with the same lead is limited to specific gear specifications. For this reason, it is impossible to arbitrarily change the helical angle of the gear material to be processed. When changing the helical angle, it was necessary to replace the male 7 and female 9 of the helical guide with the corresponding ones. As a result, it has been a constraint in gear design, and it has been difficult to flexibly cope with various types of workpieces. Further, when the restrictions are not taken into account, a great deal of labor and time are required when performing setup change of processing.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and provides a gear shaper capable of processing a plurality of types of workpieces having different helical angles without changing the setup, and eliminating restrictions on gear design to improve productivity. It is intended to provide.

[0009]

In order to achieve the above object, a first aspect of the present invention comprises a main shaft capable of reciprocating in the axial direction and rotatable around the axis, and rotating the main shaft in synchronization with the rotation of the gear material. Rotation driving means for causing the main shaft to reciprocate in the axial direction in synchronization with the rotation of the gear material, and helical rotation driving means for rotating the main shaft according to the helical angle of the gear material. It is characterized by having.

In the first invention, while the main shaft is reciprocated in the axial direction by the movement driving means, the main shaft is rotated by the rotation driving means in synchronization with the rotation of the gear material, and at the same time, the helical angle of the gear material is changed by the helical rotation driving means. The main shaft is rotated according to. When machining gear materials having different helical angles, the rotation of the main shaft by the helical rotation drive means is changed.

In order to achieve the above object, according to a second aspect of the invention, there is provided a main shaft capable of reciprocating in the axial direction and rotatable around the axis, and simultaneously rotating the main shaft in synchronization with the rotation of the gear material. Spindle rotation driving means for rotating the main shaft in combination with the synchronous rotation by adding the rotation according to the helical angle of the gear material to the main shaft, and rotating the main shaft in synchronization with the composite rotation of the main shaft. And a control means for calculating a rotation trajectory of the spindle during the composite rotation and outputting a drive command to the spindle rotation drive means.

In the second aspect of the invention, while the main shaft is reciprocated in the axial direction by the moving driving means, the main shaft is synchronously rotated in synchronization with the rotation of the gear material by the operation of the main shaft rotation driving means in accordance with a command from the control means. The rotation of the main shaft is combined with the rotation according to the helical angle of the gear material in addition to the synchronous rotation. When machining gear materials having different helical angles, the combined rotation of the main shaft is changed by changing the rotation added to the synchronous rotation to cope with the problem.

[0013] In the second invention, the control device has a function of outputting information on the rotation locus of the spindle during the composite rotation to the spindle rotation drive means as point group data at every minute time. It is characterized by being.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a schematic configuration of a main part of a gear shaper according to an embodiment of the present invention, FIG. 2 is a schematic configuration of an entire gear shaper, FIG.
4 shows a view taken along the line IV-IV in FIG. 3, FIG. 5 shows a configuration of the crank adjusting mechanism, and FIG. 6 shows a view taken along the line VI-VI in FIG. The embodiment shown in the drawings corresponds to claims 2 and 3 (second invention).

The overall structure of the gear shaper will be described with reference to FIGS.

As shown in FIG. 1, a column 12 is supported on a bed of the gear shaper 11 so as to be reciprocally movable (in the X-axis direction). The column 12 is driven by an X-axis motor 13 to reciprocate. A work table 14 is rotatably supported (around the C-axis) on the bed of the gear shaper 11, and the work table 14 includes a worm wheel 15 and a worm 1
6 through a C-axis motor 17.

On the other hand, a cutter head 18 is provided on the column 12, and a main shaft 19 is supported on the cutter head 18 so as to be rotatable (around the Y axis) and movable in the axial direction. A driven gear 20 is provided on the main shaft 19, and the driven gear 2
The drive gear 21 meshes with 0. The drive gear 21 is driven by a Y-axis motor 22, and the drive of the Y-axis motor 22 causes the main shaft 19 to rotate in a predetermined state via the drive gear 21 and the driven gear 20. That is, the Y-axis motor 2
2. The driving gear 21 and the driven gear 20 constitute a main shaft rotation driving means.

The upper end of the main shaft 19 is connected to the lower end of a connecting rod 24 via a spherical bearing 23, and the upper end of the connecting rod 24 is supported by a crank mechanism 25. The crank mechanism 25 is driven to rotate by the drive of the spindle motor 26, and the drive of the crank mechanism 25 causes the main shaft 19 to reciprocate up and down via the connecting rod 24. That is, the movement driving means is constituted by the crank mechanism 25 and the main shaft motor 26. The driving force of the spindle motor 26 is controlled by the cam mechanism 3.
0, the cutter head 18 swings via the cam mechanism 30 in accordance with the drive state of the spindle motor 26, that is, in accordance with the state of reciprocation of the spindle 19 in the vertical direction. Spindle 1
A pinion cutter (cutter) 27 is attached to the tip of the cutter 9, and the cutter 27 rotates in a predetermined state by driving the Y-axis motor 22 and reciprocates vertically by driving the main shaft motor 26.

The gear material (not shown) is a work table 14
The gear material is rotated in a predetermined state by driving the C-axis motor 17. Work table 1
The gear material is processed by the cutter 27 by the rotation of 4, the rotation of the main shaft 19, and the reciprocation in the vertical direction. The cutter 27 is reciprocated in the vertical direction by the driving of the spindle motor 26, and is rotated (synchronous rotation) in synchronization with the rotation of the gear material by the driving of the Y-axis motor 22, and the torsion angle (helical) of the gear material The rotation (composite rotation) is performed in consideration of the rotation corresponding to the angle (angle) in addition to the synchronous rotation. Also, spindle 1
When the shaft 9 is lowered, the cutter 27 is engaged with the gear material to perform processing, and when the main shaft 19 is raised, the cam mechanism 2 is moved.
The cutter head 18 swings via 7 to disengage the cutter 27 from the gear material.

By the Y-axis motor 22, the synchronous rotation with respect to the gear material and the rotation according to the torsion angle of the gear material are simultaneously combined and performed. Y-axis motor 2
2, the control device 30 controls the composite rotation of the main shaft 19, and the control device 30 calculates the rotation trajectory of the main shaft 19 during the composite rotation and outputs a drive command to the Y-axis motor 22.

An example of the calculation of the rotation locus of the main shaft 19 will be described with reference to FIG. The state of the synchronous rotation of the main shaft 19 synchronized with the rotation of the gear material can be represented by a linear state as shown by a dotted line in the figure. Further, the state of rotation of the main shaft 19 in accordance with the helical angle of the gear material can be represented by a sine curve as shown by a chain line in the figure. By adding the state of rotation according to the helical angle to the state of synchronous rotation, the state of rotation of the main shaft 19 becomes a state shown by a solid line in the figure. The rotation state of the spindle 19 shown by the solid line is output to the Y-axis motor 22. At this time, the rotation state shown by the solid line is divided for each minute time Δt, and the data of the spindle 19 is obtained as point group data for each minute time Δt. A rotation locus is calculated.

The information on the rotation locus of the main shaft 19 calculated in this manner is output from the control device 30 to the Y-axis motor 22 as data of a point group at every minute time Δt, and the rotation indicated by the solid line in FIG. The main shaft 19 rotates in the state of the trajectory. Thus, by the driving of one Y-axis motor 22, the synchronous rotation with respect to the gear material and the rotation according to the torsion angle of the gear material are simultaneously synthesized, so that the main shaft 19 is combinedly rotated.

The control device 30 stores information on the rotation trajectory of the main shaft 19 calculated as the data of the point group for each minute time Δt for a plurality of gear materials having different helical angles. When the gear material is changed, the information of the rotation trajectory of the main shaft 19 according to the changed gear material is called out, and the information of the new rotation trajectory of the main shaft 19 is transmitted from the control device 30 as data of a point group for each minute time Δt. Output to the Y-axis motor 22. For this reason, when the gear material is changed, by inputting information of a new gear material to the control device 30,
The rotation locus of the main shaft 19 can be changed without mechanically changing the setup. Therefore, machining of a plurality of types of gear materials can be easily performed, and flexible handling of a variety of types of gear materials can be achieved.

In the above-mentioned embodiment, the rotation according to the helical angle of the gear material is combined with the synchronous rotation by the single Y-axis motor 22 to perform the compound rotation. A helical rotation drive unit that performs rotation according to the angle may be separately provided (claim 1: first invention). Even in this case, the rotation locus of the main shaft 19 can be changed without performing mechanical setup change.

Next, the essential configuration of the gear shaper of this embodiment will be described in detail with reference to FIGS.

As shown in FIG. 3, a cutter 27 is mounted on the lower end of the spindle 19, and the spindle 19 is slidably guided in the axial and rotational directions via a bearing 31 fitted to the cutter head 18. Have been. Male 32 on the upper part of the main shaft 19
Are fitted, and a convex spline 33 extending in the axial direction (vertical direction) is formed on the outer peripheral surface of the male shape 32. A guide cylinder 34 is arranged outside the male shape 32, and a concave groove 35 extending in the axial direction (vertical direction) is formed on the inner peripheral surface of the guide cylinder 34. Male type 32 is spline 3
It is slidably guided in the guide cylinder 34 vertically through the groove 3 and the groove 35 of the guide cylinder 34. The guide cylinder 34 is rotatably supported by the cutter head 18 via a bearing 36, and the driven gear 20 is fixed to an upper portion of the guide cylinder 34.

The cutter head 18 is provided with a Y-axis motor 22, and a driving gear (not shown) of the Y-axis motor 22 meshes with the driven gear 20. When the Y-axis motor 22 is driven, the main shaft 19 rotates along the above-described composite rotation locus via the driven gear 20, the guide cylinder 34, and the male shape 32.

On the other hand, the housing 3
The spherical bearing 23 is rotatably and swingably supported on the housing 37. The lower end of the feed screw shaft 39 is connected to the spherical bearing 23, and the axial position of the screw portion 40 of the feed screw shaft 39 is fixed in a state of being screwed to the knuckle 41. The knuckle 41 is rotatably supported on the rotating disk 42 side of the crank mechanism 25, and the rotation of the rotating disk 42 causes the main shaft 19 to move vertically through the knuckle 41, the feed screw shaft 39, the spherical bearing 23, the housing 37 and the male shape 32. To reciprocate. That is, the connecting rod 24 is configured by the knuckle 41 and the feed screw shaft 39.

By rotating the turntable 42 by driving the spindle motor 26 (not shown in FIG. 3), the spindle 19 reciprocates vertically via the connecting rod 24 and the spherical bearing 23. At this time, the male shape 32 is slidably guided in the guide cylinder 34 via the spline 33 and the groove 35 of the guide cylinder 34, and the main shaft 19 reciprocates in the vertical direction. The combined rotation of the spindle 19 driven by the Y-axis motor 22 and the spindle 19 driven by the spindle motor 26 described above.
With the reciprocating movement of the gear, machining of the gear material by the cutter 27 is performed.

In the above-described gear shaper, it is necessary to adjust the position of the vertical movement end and the vertical movement stroke of the cutter 27 due to wear of the cutter 27, change of gear material, and the like. For this purpose, an adjusting mechanism for adjusting the upper and lower end positions of the main shaft 19 during reciprocating motion and an adjusting mechanism for adjusting the support position of the knuckle 41 with respect to the rotary plate 42 are provided. By changing the screwing state of the feed screw shaft 39 to the knuckle 41 by the adjusting mechanism, the upper and lower end positions of the main shaft 19 during reciprocation are adjusted, and by changing the supporting position of the knuckle 41 to the turntable 42 by the adjusting mechanism. The stroke at the time of reciprocation of the main shaft 19 is adjusted. Hereinafter, the upper and lower end position adjusting mechanism and the stroke adjusting mechanism will be described in detail.

A mechanism for adjusting the upper and lower end positions of the main shaft 19 when reciprocating will be described with reference to FIGS. The feed screw shaft 39 and the main shaft 19 are rotatably supported via the spherical bearing 23. Therefore, when adjusting the upper and lower end positions of the spindle 19 during reciprocation, the feed screw shaft 39 and the spindle 19 are adjusted.
Are fixed to each other in the rotation direction, and the screwing state of the feed screw shaft 39 to the knuckle 41 is changed.

That is, the housing 37 is provided with a gear 43 coaxial with the main shaft 19, and the feed screw shaft 39 is provided with a gear 4
A gear 44 having the same diameter as the gear 3 and coaxial with the feed screw shaft 39 is provided. The gear 43 and the gear 4 are provided on the cutter head 18 side.
A drive pinion 49 that can simultaneously mesh with the drive pinion 4 is supported, and the drive pinion 49 is movable toward and away from the housing 37 by a cylinder 50.

When the main shaft 19 is driven to rotate, the drive pinion 45 is moved away from the gears 43 and 44 so as not to mesh with the gears 43 and 44, so that the main shaft 19 and the feed screw shaft 39 are rotatable with each other. When the drive pinion 49 is meshed with the gear 43 and the gear 44 by driving the cylinder 50, the main shaft 19 and the feed screw shaft 39 are integrated via the drive pinion 49, and the main shaft 19 and the feed shaft 19 are fed by the rotation of the drive pinion 49. The screw shaft 39 rotates integrally.

As shown in FIG. 4, the knuckle 41 is formed with a female screw part 45 into which the screw part 40 of the feed screw shaft 39 is screwed, and the knuckle 41 is divided into two parts.
Has been split. Two pins 46 are inserted into the divided knuckles 41, and the two pins 46 are urged in a direction of tightening the knuckles 41 divided by the disc springs 47, that is, in a direction of reducing the diameter of the female screw portion 45. Have been. As a result, the screw portion 40 of the feed screw shaft 39 screwed to the female screw portion 45 is in a state where rotation is restricted.

Each of the two pins 46 is provided with a piston 48, and pressure oil is applied to the piston 48 from a supply source (not shown). By applying pressure oil to the piston 48, the pin 46 moves to the left in the drawing against the urging force of the disc spring 47, and the divided knuckle 41 is loosened. Knuckle 41 divided
Is loosened and the diameter of the female screw portion 45 is increased, so that the screw portion 4 of the feed screw shaft 39 screwed to the female screw portion 45 is screwed.
0 becomes freely rotatable. Normally, no pressure oil acts on the piston 48, and the feed screw shaft 39 is fixed to the knuckle 41.

When adjusting the upper and lower end positions of the main shaft 19 during reciprocation, the drive pinion 45 is meshed with the gears 43 and 44 by driving the cylinder 46. In this state, pressure oil is applied to the piston 48 to loosen the divided knuckle 41 and increase the diameter of the female screw portion 45. The drive pinion 45 is driven to rotate the feed screw shaft 39 and the main shaft 19 integrally via the gears 43 and 44. By the rotation of the feed screw shaft 39, the feed screw shaft 39 and the main shaft 19 move integrally in the axial direction via the screw portion 40 and the female screw portion 45, and the upper and lower end positions of the main shaft 19 when reciprocating are adjusted. After adjusting the upper and lower end positions by rotating the feed screw shaft 39 in a predetermined state, the pressurized oil acting on the piston 48 is released, and the divided knuckle 41 is tightened by the urging force of the disc spring 47, and the feed screw shaft 39 is rotated. It is fixed to the knuckle 41.

Thus, the feed screw shaft 39 and the main shaft 1
The upper and lower end positions of the main shaft 19 during reciprocation are adjusted by integrally moving the shaft 9 in the axial direction, so that it is possible to cope with wear of the cutter 27, change of gear material, and the like.

Next, a stroke adjusting mechanism for reciprocating the main shaft 19 will be described with reference to FIGS. The knuckle 41 can adjust the supporting position with respect to the rotating disk 42, that is, the amount of eccentricity. By changing the amount of eccentricity with respect to the rotating disk 42, the stroke of the main shaft 19 during reciprocating movement is adjusted.

That is, the turntable 42 is rotatably supported via a bearing 51, and a gear 52 is provided behind the turntable 42 (upper in FIG. 6). The gear 52 is the main shaft motor 26
And the rotating disk 42 is rotated by the driving of the spindle motor 26. A slider 54 is provided on the turntable 42 so as to be slidable in the radial direction. As shown in FIG. 6, the upper end of the knuckle 41 is rotatably supported on the slider 54 via a bearing 55.

A screw shaft 56 extending in the sliding direction of the slider 54 is rotatably supported on the turntable 42, and the upper end of the screw shaft 56 projects above the turntable 42. A nut 57 is screwed into the screw shaft 56 inside the turntable 42, and the nut 57 is fixed to the slider 54. That is, the rotation of the screw shaft 56 causes the slider 54 to move radially with respect to the turntable 42 via the nut 57,
The reciprocating stroke of the main shaft 19 is adjusted.

At four positions of the rotary disk 42, fixed pistons 59 are provided which are fitted to the side edges 58 of the slider 54 to fix the sliding position of the slider 54 with respect to the rotary disk 42. The fixed piston 59 is urged by a disc spring 60, and the sliding position of the slider 54 is fixed by urge of the fixed piston 59 by the disc spring 60. Pressure oil is supplied to the fixed piston 59 from a supply source (not shown). When the pressure oil is supplied to the fixed piston 59, the fixed piston 59 moves against the urging force of the disc spring 60, and the side edge of the slider 54 is moved. The fitting to the part 58 is released. Normally, the fixed piston 59 is urged by the disc spring 60 and fitted to the slider 54, and the sliding position of the slider 54 with respect to the rotary plate 42 is fixed.

On the other hand, as shown in FIG. 5, a gear 61 is provided at the upper end of a screw shaft 56 projecting above the turntable 42. A housing 63 is fixed to the upper frame 62, and a cylindrical gear 65 is rotatably supported in the housing 63 via a bearing 64.

A screw shaft 66 is supported in the cylindrical gear 65 in a state that it is movable in the axial direction (vertical direction in the figure) and is fixed in the rotational direction. The lower end of the screw shaft 66 can mesh with the gear 61. Gear 67 is provided. The screw shaft 66 is moved up and down by driving means (not shown).
The gear 67 meshes with the gear 61 when 6 moves to the lowermost end. A drive gear 69 is provided in the housing 63.
Are provided, and the drive gear 69 meshes with the cylindrical gear 65.

That is, when the screw shaft 66 moves to the lowermost end and the drive gear 69 is driven in a state where the gear 67 and the gear 61 mesh with each other, the screw shaft 56 is driven via the cylindrical gear 65 and the screw shaft 66. The slider 54 rotates so that the slider 54 slides with respect to the turntable 42. Normally, screw shaft 6
6 moves upward, and the gear 67 and the gear 61 are not meshed.

When adjusting the vertical movement stroke of the main shaft 19, the screw shaft 66 is moved downward by a driving means (not shown), and the gear 67 is engaged with the gear 61 of the screw shaft 56. The pressurized oil is supplied to the fixed piston 59 and the slider 5
4 and the slider 54 is
Is slidable. When the drive gear 69 is driven in this state, the screw shaft 56 rotates via the cylindrical gear 65, the screw shaft 66, the gear 67, and the gear 61. Screw shaft 56
Is rotated, the slider 5 is moved via the nut 57.
4 moves in the radial direction with respect to the turntable 42.

After the slider 54 is moved to a predetermined position, the supply of pressure oil to the fixed piston 59 is released, and the fixed piston 59 is moved by the urging force of the disc spring 60.
And the position of the slider 54 with respect to the turntable 42 is fixed. After the position of the slider 54 is fixed, the screw shaft 66 is moved upward by a driving means (not shown), and the engagement between the gear 61 and the gear 67 of the screw shaft 56 is released.

In this manner, by changing the position of the slider 54 with respect to the rotary disk 42, the stroke of the main shaft 19 at the time of reciprocating movement is adjusted, and it is possible to cope with the change of the cutter 27 and the gear material. .

The above-described gear shaper 11 synchronizes the main shaft 19 with the rotation of the gear material by driving the Y-axis motor 22 in accordance with a command from the control means 30 while reciprocating the main shaft 19 in the axial direction by the crank mechanism 25. Simultaneously with the rotation, the main shaft 19 is combined with the rotation corresponding to the helical angle of the gear material in addition to the synchronous rotation, so that the synchronous rotation of the main shaft 19 with respect to the gear material and the helical angle by one Y-axis motor 22 are performed. And rotation according to.

As a result, when machining gear materials having different helical angles, the combined rotation of the main shaft 19 can be changed by changing the rotation in consideration of the synchronous rotation. Machining can be easily performed without mechanical setup change, and it is possible to flexibly cope with various kinds of gear materials.

[0050]

According to the first aspect of the present invention, there is provided a gear shaper comprising: a rotation driving means for rotating a main shaft in synchronization with rotation of a gear material; a movement driving means for reciprocating the main shaft in an axial direction in synchronization with rotation of a gear material; Since helical rotation driving means for rotating the main shaft in accordance with the helical angle of the gear material is provided, the rotation locus of the main shaft can be changed to an arbitrary state by the helical rotation driving means. As a result, gear materials with different helical angles can be machined without mechanical setup change, enabling flexible handling of various types of gear materials, eliminating restrictions on gear design. Productivity can be improved.

In the gear shaper according to the second aspect of the present invention, the main shaft is synchronously rotated in synchronization with the rotation of the gear material, and at the same time, the main shaft is rotated by taking into account the rotation corresponding to the helical angle of the gear material in synchronization with the rotation. Main shaft rotation driving means for performing composite rotation, movement driving means for reciprocating the main shaft in the axial direction in synchronization with the composite rotation of the main shaft, and calculating the rotation trajectory of the main shaft at the time of the composite rotation and issuing a drive command to the main shaft rotation driving means. With the control means for outputting, the rotation locus of the spindle including the synchronous rotation can be changed to an arbitrary state by one spindle rotation driving means based on the drive command of the control means.
As a result, it is possible to process multiple gear materials with different helical angles without mechanical setup change and without increasing the size of the equipment, enabling flexible handling of various types of gear materials. Thus, there is no restriction on gear design, and productivity can be improved.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a main part of a gear shaper according to an embodiment of the present invention.

FIG. 2 is a schematic configuration diagram of the entire gear shaper.

FIG. 3 is a cross-sectional view illustrating a configuration of a main part of a gear shaper.

FIG. 4 is a view taken along line IV-IV in FIG. 3;

FIG. 5 is a configuration diagram of a crank adjustment mechanism.

FIG. 6 is a view taken along line VI-VI in FIG. 5;

FIG. 7 is a graph showing a rotation state of a main shaft.

FIG. 8 is a schematic configuration diagram of a main part of a conventional gear shaper.

FIG. 9 is a cross-sectional view illustrating a configuration of a main part of a conventional gear shaper.

[Explanation of symbols]

 Reference Signs List 11 gear shaper 13 X-axis motor 17 C-axis motor 18 cutter head 19 main shaft 22 Y-axis motor 23 spherical bearing 24 connecting rod 25 crank mechanism 26 main shaft motor 27 pinion cutter (cutter) 30 control means 32 male 33 spline 34 guide cylinder 39 feed Screw shaft 41 Knuckle 42 Turntable

Claims (3)

[Claims] A main shaft rotatable reciprocally in the axial direction and rotatable around the axis; a rotation driving means for rotating the main shaft in synchronization with the rotation of a gear material; and the main shaft in synchronization with the rotation of the gear material. Moving drive means for reciprocating the shaft in the axial direction,
Helical rotation driving means for rotating the main shaft according to the helical angle of the gear material. 2. A main shaft reciprocally movable in the axial direction and rotatable around the axis, and the main shaft is synchronously rotated in synchronization with the rotation of a gear material, and the rotation of the gear material according to a helical angle is synchronized with the synchronization. Main shaft rotation driving means for rotating the main shaft in combination with rotation to compositely rotate the main shaft,
Movement drive means for reciprocating the spindle in the axial direction in synchronization with the composite rotation of the spindle, and control for calculating a rotation trajectory of the spindle during the composite rotation and outputting a drive command to the spindle rotation drive means And a gear shaper. 3. The control device according to claim 2, wherein:
A gear shaper having a function of outputting information on the rotation trajectory of the spindle during the composite rotation to the spindle rotation drive means as point group data for each minute time.