JPS6215008A - Automatic stepless regulating helical guide for gear shaper - Google Patents

Abstract

PURPOSE:To make a wide variety of helical gears machinable with one guide as well as to aim at improvement in production efficiency, by making a helical angle of the helical guide of a gear shaper regulable in a stepless way. CONSTITUTION:A gear cutter is attached to the tool shank 31 installed in a spindle 34. Operating a clutch 61, a gear wheel 57 is driven for rotation by a stepping motor 62 via gears 60, 59 and 58. This rotation is transmitted to a worm wheel 47 via a worm 51, whereby a tilt angle (helical angle ) to an axial center of the spindle 34 of a guide member 46 is regulated. A tilt angle regulating amount is detected by a pulse to be outputted from a pulse coder 67, thus automatic regulation of the helical angle is easily performable.

Description

DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a helical guide for a gear shaper, and is capable of automatically and steplessly adjusting the helical angle.

<Prior art> As shown in FIG. 4, which shows a cross-sectional side view of the helical guide mechanism of a gear shaper, a main shaft 2 on which a gear cutting tool l is attached is movable back and forth in the axial direction and rotatable using a hydrostatic bearing 3. The connecting rod 4 is guided by a crank mechanism and reciprocated in the axial direction via a spherical bearing 5. A male helical guide 6 as shown in perspective in FIG. 5 is fixed to the main shaft 2, and a female helical guide 8 fitted to the flange 7
The Yoshios type 6 is guided, and the main shaft 2 rotates reciprocatingly when reciprocating in the axial direction. The flange 7 is rotated in synchronization with the helical gear, which is a workpiece, during gear cutting by a worm wheel 9 and a worm (not shown). In such a helical guide mechanism, a male type 6 and a female type 8 of the helical guide are used.
Unless the helical gear is replaced, it is impossible to change the helical angle when machining the helical gear, and it is subject to design constraints.1. Alternatively, there is a problem that the processing setup change time becomes extremely long.

In order to eliminate such problems, a helical guide of a gear shaver is used which allows the helical angle to be changed and adjusted as shown in FIGS. 6-7. As shown in the figure, the main shaft 11 is capable of reciprocating in the axial direction, and a pinion 12 is coaxially fixed to the main shaft 11.

The pinion 12 is connected to the main shaft 11 by the upper and lower holders lla and llb.
The main shaft 111 is fixed in the axial direction, and a key 13 prevents the main shaft 111 from rotating.

The rack 14 meshes with the pinion 12, and the holders lla,
n pinion 12 restrained in the axial direction of the main shaft 11 by llb
It is slidably guided in the tangential direction of the pitch circle of n. The rack 14 has a slider 1 centered around an axis 15 perpendicular to the main axis 11.
6, and the slider 16 is fitted into a dovetail groove of a guide member 17. Guide member 17 Ring gear 18
The ring gear 18 is fixed to n, and the ring gear 18 meshes with the drive pinion 19.

That is, by rotating the drive pinion 19, the ring gear 18 is rotated, and the inclination of the guide member 17 with respect to the main shaft 11 can be changed. The ring gear 18 is positioned using positioning holes 20a, 20b, 20.
By connecting c and the hole 21 of the ring gear 18 with a positioning pin (not shown), this can be done with high precision.

In the helical guide having the above configuration, the guide member 17 is connected to the main shaft 11.
When the main shaft 11 is reciprocated in the axial direction, the rack 14 is moved to the holder lla.

It slides along the guide member 17 together with the slider 16 via the slider 11b. At this time, the rack 14 is rotatably supported by the slider 16, so the rack 14 and pinion 12 remain in an engaged state, and as the rack 14 slides in the inclined direction along the guide member 17, the rack 14 14 moves in the tangential direction of the pinion 12, the pinion 12 rotates in response to the amount of 5, and the main shaft 11 rotates. The amount of movement of the rack "14 in the tangential direction of the pinion 12 changes depending on the inclination angle of the guide member 17 with respect to the main shaft 11, and the amount of rotation of the main shaft can be changed, making it possible to process helical gears of multiple stocks with different helical angles. Can be applied.

<Problems to be Solved by the Invention> The helical guide capable of changing and adjusting the helical angle described above has a guide member 1 for determining the helical angle.
7 is fixed by connecting the positioning hole 20 with the hole 21 of the ring gear 18 using a positioning pin, so the helical angle cannot be adjusted steplessly.

Therefore, there are design constraints on the helical gear. Also,
It is difficult to automatically adjust the helical angle. That is, in order to automatically adjust the helical angle, it is necessary to provide a drive source for the drive pinion 19, but since the main shaft 11 needs to rotate in synchronization with the helical gear during machining, the blow gear 18, drive pinion 19
The main shafts ll and 7 are also rotated synchronously. Therefore, the drive sources, such as the drive vinyl off 19, must also be rotated synchronously.

Wiring becomes difficult. Further, during processing, it is necessary to lock the ring gear 18 so that it does not move due to the reaction force from the slider 16.

In the case of heat, there is also a problem with the holding torque of the drive source.

The present invention has been made in view of the above situation.

We provide a gear shaper helical guide that can automatically and steplessly adjust the helical angle, making it possible to process many types of helical gears with different helical angles without replacing the helical guide. The purpose of this invention is to reduce constraints, shorten machining setup changeover time, and improve production efficiency.

〈Problem + Means for resolving S〉 The structure of the present invention for achieving the above object is as follows.

The main shaft rotates with a rotation center axis extending in the same direction as the rotation center axis of the workpiece support rotation shaft provided on the main spindle head, and moves reciprocally in the axial direction.The main shaft rotates in synchronization with the workpiece support rotation shaft. a flange that rotates synchronously with the workpiece support rotating shaft about the same axis as the rotation center axis of the main shaft; a pinion that is coaxially fixed to the main shaft; and a flange that meshes with the pinion in the axial direction of the main shaft. a rack that is restrained by the pinion and can slide in the tangential direction of the pinion; and the rack I is rotatably supported by a shaft turning force perpendicular to the sliding direction of the rack and perpendicular to the moving direction of the main shaft. a slider, a guide member that supports the slider so as to be able to reciprocate in one direction parallel to the moving direction of the main shaft, and a central axis of rotation of the slider in the same direction as the rotation axis of the slider relative to the rack; A worm wheel extends and has a side surface fixed to the guide member and is supported by the flange.A rotation center shaft extends in the same direction as the rotation center axis of the main shaft, and a small gear is provided at the end of the rotation center shaft and meshes with the worm wheel. A worm, a large gear rotatably supported by the flange with a rotary shaft coaxial with the rotational center axis of the main shaft and meshing with the small gear, and a driving means connected via a blue clutch provided on the main shaft head. It is characterized by a drive gear that meshes with the large gear.

<For production> Drive gear of drive means, large gear.

The worm rotates via the small gear, and the rotation of the worm rotates the worm wheel and tilts the guide member. Since the rack is rotatable relative to the slider, the meshing state between the rack and pinion is maintained even if the guide member is tilted. When the main shaft is reciprocated in the axial direction, the rack moves along the guide member along with the slider in the inclined direction as the main shaft moves, and as the rack moves in the inclined direction, the rack moves in the tangential direction of the pinion. The pinion rotates in response to the amount of rotation, and the main shaft rotates. By changing the rotation f of the guide member, the amount of movement of the pinion of the rack in the tangential direction when the main shaft moves in the axial direction changes, and the amount of rotation of the main shaft can be changed. The drive means is installed in the spindle head, so during machining, the drive gear is rotated around the large gear by one clutch, and the transmission of force between the worm and the worm wheel is irreversible, so sliding The reaction force from the child is not transmitted from the worm wheel to the worm.

Embodiment> FIG. 1 shows a cross-sectional side view of an automatic stepless adjustment helical guide for a gear shaper according to an embodiment of the present invention, and FIG.
...−... line cross section in the figure.

FIG. 3 shows details of the arrow portion in FIG. 1.

A gear cutting tool (not shown) is attached to the lower end of the tool shaft 31, and the tool shaft 31 is axially slidably and rotatably supported by a spindle head 33 via a hydrostatic bearing 32. I'm n.

Taber shank portion 31aG at the top of the tool shaft 31; C main shaft 3
4 fits into the lower tapered hole 34a, and connects the tool shaft 31 and the main shaft 3.
4 is prevented from rotating by a key 35, and the tapered shank portion 31a receives an axial tensile force from the bolt 36, and is firmly fitted into the tapered hole 34a. The main shaft 34 is capable of reciprocating in the axial direction via a spherical bearing 38 by a connecting a-rad 37 driven by a crank mechanism.
A pinion 39 is coaxially fixed to the main shaft 341. The pinion 39 is narrowed by upper and lower holders 40a and 40b, and is fixed in the axial direction of the main shaft 34 by a nara) 41.
A key 42 prevents rotation of the main shaft 34.

The rack 43 meshes with the pinion 39, and the holder 4oa,
The pinion 3 is restrained in the axial direction of the main shaft 34 by the 40b.
It is slidably guided in the tangential direction of the pitch circle of 9.

The rack 43 is rotatably supported by a slider 45 about an axis 44 perpendicular to the main shaft 34, and the slider 45 is supported by a guide member 46.
It fits into the dovetail groove. wife! l. When the main shaft 34 moves in the axial direction, the rack 43 and slider 45 move along the main shaft 34.
As the guide member 46f moves, the guide member 46f moves along with the movement of the guide member 46f. The guide member 46 is fixed to the side surface of a worm wheel 47 whose central axis of rotation extends in the same direction as the central axis of the shaft 44, and the amount of rotation of the worm wheel 47 corresponds to the amount of tilt of the guide member 46. Is the worm wheel 47 a bearing 48? ! The flange 49 is rotatably supported by the flange 49 through the main shaft 33#, and the flange 49 is rotatably supported by the main shaft 33# through the main shaft 34.
This is supported. A worm wheel 50 is provided on the flange 49, and the flange 49 is in contact with the gear to be cut through a worm (not shown) during machining.

A worm 51 whose rotation center axis extends in the same direction as the rotation center axis of the main shaft 340 is rotatably supported on the flange 49.
The worm 51 meshes with the worm wheel 47. A small gear 52 is attached to the top of the worm 51. A plate 53 is fixed to the upper part of the flange 49, and a small flange 54 is fixed to the plate 53. A metal bearing 5 is installed between the plate 53 and the small flange 54.
5.56, a large gear 57 is rotatably supported, and the rotation center axis of the large gear 570 is the same as the rotation center axis of the main shaft 340. The large gear 57 meshes with the small gear 52. A drive gear 58 meshes with the large gear 57 in a phase different from that of the small gear 52 in the axial direction, so that even if the flange 49 rotates, the small gear 52 and the drive gear 58 do not collide. The drive gear 58 is coaxially fixed to an intermediate gear 59, and an output gear 60 meshes with the intermediate gear 591. The output gear 60 is connected via a clutch 61 to the output shaft of a stepping motor 62, which is a driving means. Drive gear 58, intermediate gear 59, and output gear 60 are bearings 63 and 64%
It is stored in the gear box 65 through the gear box 65.
is attached to the main shaft via the frame 66 to the rad 33.

A pulse coder 67 is attached to the gear box 65, and a movable element 68 of the pulse coder 67 is fixed to the intermediate gear 60.

A plurality of spring plungers 69 are screwed into the small flange 541. Spring plunger 6
As shown in FIG. 3, which shows the enlarged state of the cylinder 9, a cylinder 70 is provided with a screw thread on its outer diameter. Consisting of a spring 71 and a plunger 72 whose tip is semispherical,
The tip of the plunger 72 can be fitted into a plurality of notched holes 73 formed in the end face of the large gear 57. A large number of notched holes 73 are bored at equal pitches in the circumferential direction of the end face of the large gear 57.

The upper outer circumferential surface of the main shaft 34 is slidable and rotatable in the axial direction by a bearing metal 74 fitted to the small flange 54 (this is supported by the main shaft generated by the radial force that the pinion 39 receives from the rack 43 force 1). 34 is minimized.

Next, the principle and operation of the automatic stepless adjustment helical guide with the above configuration will be explained. Adjust the helical angle when not cutting gears.In this case, adjust the flange 49.
The rotational drive of the connecting pad 37 and the driving of the connecting pad 37 are not performed. Clutch 61 is operated, output gear 60. Intermediate gear 59. When the large gear 57 is rotationally driven by the stepping motor 62I via the drive gear 58, the plunger 72 of the spring plunger 69 is raised from the notch hole 73. The rotation of the large gear 570 is transmitted to the worm wheel 47 via the small gear 52° and the worm 51, and the inclination angle of the guide member 46 with respect to the axis of the main shaft 34 is adjusted. When the main shaft 34 moves L in the axial direction with the guide member 461 inclined at an angle θ with respect to the axis of the main shaft 34, the slider 45 moves to the inclined guide member 46 as the main shaft 34 moves.
As a result, the rack 43 slides along the pinion 39
It moves in the tangential direction ζ by L sin θ.

Here, the notched holes 73 have a pitch of a6d"/n.
The rotation angle of the stepping center 62 is also 360°/n in terms of the rotation angle of the large gear 570.
It receives a rotation command pulse that rotates in a stepwise manner. Although the stepping motor 62 rotates in a stepwise manner, the inclination angle of the guide member 46, that is, the helical angle, can be considered to be infinitely adjusted in practice. This is because by increasing the reduction ratio of the worm 51 and the worm wheel 47, a s d' /n, which is the unit of the minimum rotation angle of the large gear 57, can be converted into the inclination angle of the guide member 46. This is because the angle is small enough to cause no practical problems.

By disengaging the clutch 61 during gear cutting, the large gear 5 is rotated synchronously with the workpiece of the flange 49.
Even if the drive gear 58.7 rotates, the drive gear 58. Intermediate gear 59. The output gear 60 only rotates in parallel. The large gear 57 is the intermediate gear 59. Even when subjected to friction torque of the bearings 63 and 64 that support the output gear 60 and vibrations of the machine.

Since the large gear 57 is positioned and fixed to the flange 49 by the 69 spring plungers, the large gear 57 and the small gear 52 are prevented from rotating relative to each other during gear cutting. Furthermore, due to the irreversible nature of force transmission between the worm 51 and the worm wheel 47, the worm 51 is not rotated even if the worm wheel 47 receives a reaction force from the slider 45 during gear cutting. The helical angle is held constant.

The adjustment amount when adjusting the helical angle is Pulsecoder 67.
The large gear 57 can be detected by counting the pulses output from the machine with a pulse counter (not shown) of a machine control device.
Automatic adjustment of the helical angle becomes easier if the control device memorizes the number of times n of the rotation.

Furthermore, a stepping motor 62 and a pulse coder 67
Since it is provided on the machine body side, processing of power lines and signal lines is also easy.

Although the stepping motor 67 is used as the driving means in the above embodiment, the present invention is not limited to the above embodiment, such as using a digitally actuated cylinder operated via a pinion rack and a one-way clutch. Effect> Since the automatic stepless adjustment helical guide of the gear shaper of the present invention can automatically adjust the helical angle steplessly, it is possible to process many types of helical gears with different helical angles without replacing the helical guide. Become.

As a result, the constraints on the design of the helical gear are reduced, and the machining setup change time is shortened, making it possible to improve production efficiency.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional side view of an automatic stepless adjustment helical guide for a gear shaver according to an embodiment of the present invention. Figure 2 is a sectional view taken along the river line -■ in Figure 1, Figure 3 is a detailed view of the arrow I section in Figure 1, Figure 4 is a cross-sectional side view of a conventional helical guide mechanism, and Figure 5 is a helical guide mechanism. Figure 6 is a perspective view of the male guide.
A partially cutaway side view of the i'@ helical guide, FIG. 7 is a view taken in the direction of the X arrow in FIG. In the drawing, 33 is the spindle head. 34 is the main axis. 39 is pinion. 43 is a rack. 45 is a slider. 46 is a guide member, 47 is a worm wheel. 49 is a flange. 51 is warm. 52 is a small gear. 57 is a large gear. 58 is a drive gear. 61 is the clutch. 62 is a stepping motor.

Claims (1)

[Claims] A main shaft that rotates with a rotation center axis extending in the same direction as the rotation center axis of the workpiece support rotation shaft provided on the main spindle head, moves back and forth in the axial direction, and rotates synchronously with the workpiece support rotation shaft; , a flange that rotates around the same axis as the rotation center axis of the main shaft and synchronously with the rotating shaft for supporting the workpiece; a pinion that is coaxially fixed to the main shaft; and a pinion that meshes with the pinion and rotates in the axial direction of the main shaft. a rack that is restrained and can slide in the tangential direction of the pinion; and a slider that is rotatably supported by the rack around an axis perpendicular to the sliding direction of the rack and perpendicular to the moving direction of the main shaft. a guide member that supports the slider so as to be able to reciprocate in one direction parallel to the direction of movement of the main shaft; and a guide member whose central axis of rotation extends in the same direction as a rotation axis of the slider relative to the rack. a worm wheel whose side surface is fixed to and supported by the flange; a worm whose rotation center axis extends in the same direction as the rotation center axis of the main shaft and a small gear is provided at the end of the rotation center axis and meshes with the worm wheel; A large gear that is rotatably supported by the flange around the same axis as the rotation center axis of the main shaft and meshes with the small gear, and a drive that is connected via a clutch to a drive means provided on the main shaft head and meshes with the large gear. Automatic stepless adjustment helical guide for gear shaper equipped with gears.