JPS62124819A - Generating device for unspecified lead of gear shaper - Google Patents

Abstract

PURPOSE:To improve production efficiency, by eliminating the necessity for using a helical guide and reducing a time of rearrangements for machining plural kinds of helical gears having a different helical angle. CONSTITUTION:Power 29 is transmitted by the same crankshaft 23 to a crank mechanism 24 vertically moving a main spindle 2 and a crank mechanism 23 giving rotation to a planet gear supporting case 21. A vertically moving speed of the main spindle 2 and a rotary speed, given to the case 21, draw a sinusoidal curve, and the same rotation to that, when a helical guide is used, is given to the main spindle 2 in any of its position in the vertical direction, thus a helical gear of different helical angle can be efficiently machined by a tool 1 by optionally setting a twist amount and a twist direction.

Description

DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to an unspecified lead generating device in a gear shaper.

<Prior Art> As shown in FIG. 2, 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 1 is mounted is movable back and forth in the axial direction and rotatable by a hydrostatic bearing 3. It is guided and reciprocated in the axial direction via a spherical bearing 5 by a connecting q-piece 4 driven by a crank mechanism. A male helical guide 6, as shown in perspective in FIG. It rotates back and forth when reciprocating in the axial direction. A worm wheel 9 is provided on the flange 7, and the worm wheel 9 meshes with a worm 10 provided on the machine side, as shown in FIG. The flange 7 is rotated by the rotation of the worm 10 via a worm wheel 9 in synchronization with the helical gear that is the workpiece during gear cutting. In this case, the worm 10 is fixed in the axial direction. Here, the lead length of the helical guide and the pitch circle diameter d of the gear cutting tool 1. There is a relationship with P as shown in the following formula.

π= dop= L-ψ...(1)
In addition, ψ is the helix angle of the gear cutting tool 1, and mo is the gear cutting tool 1.
, where Z is the number of teeth of the gear cutting tool 1.

Therefore, the torsion angle that can be processed for one helical guide is limited to the case where dcp is a certain range and Z satisfies the condition that Z is an integer.

<Problems to be Solved by the Invention> In the helical guide mechanism described above, it is impossible to change the helical angle when machining gears unless the male type 6 and female type 8 of the helical guide are replaced. There are problems in that the above limitations are imposed or the time required for changing machining setups is extremely long.

The present invention has been made in view of the above situation, and provides an unspecified lead generation device for a gear shaper that can steplessly adjust the helical angle, thereby allowing multiple types of different helical angles to be created without replacing the guide member. The purpose of the present invention is to make it possible to process helical gears, eliminate the need for expensive helical guides that are difficult to manufacture, and improve production efficiency by shortening processing setup change time.

Means for Solving Interstitial Layer Points> The configuration of the present invention for achieving the above object is such that the crank member is rotated with a rotation center axis extending in the same direction as the rotation center axis of the workpiece support rotation shaft. An unspecified lead generation device for a gear shaper that is equipped with a cutter main shaft that reciprocates in the axial direction through , an output system of a differential gear device whose input system and output system are connected via a planetary gear member is connected to the guide member, and an input system of the differential gear device is connected to a rotational drive system of the cutter main shaft. and in order to add lead generation rotation to the output system, the crank member is connected to the planetary gear member side of the differential gear device via a crank mechanism capable of arbitrarily transmitting the power of the crank member. Features.

Function> When the power of the crank member is not transmitted to the planetary gear member,
The input system and output system of the differential gear device rotate at the same time, and the power from the rotary drive system is directly transmitted to the cutter main shaft via the guide member, and the cutter main shaft rotates in synchronization with the rotation of the rotating shaft for supporting the workpiece. Applicable to machining gears that reciprocate while rotating and have no helix angle. When the power of the crank member is transmitted to the planetary gear member via the crank mechanism, the output system of the differential gear device rotates with the power of the crank member added, and the cutter main shaft rotates with the power of the crank member added. The power from the system is transmitted through the guide member, and the cutter main shaft rotates and reciprocates with a fixed amount of twist relative to the rotation of the rotating shaft for supporting the workpiece, and is applied to machining gears having a helix angle. The twist t and direction of the cutter main shaft are arbitrarily determined by adjusting the crank mechanism.

<Embodiment> FIG. 1 shows a schematic configuration diagram of an unspecified lead generation device for a gear shaper according to an embodiment of the present invention, and the same components as those in the conventional system are given the same reference numerals and redundant explanations will be omitted. is omitted.

A male type 11 which is a guide member with an infinite lead (twist angle of 0 degrees) is fixed to the main shaft 2 which is the cutter main axis, and the male type 11 is attached to a female type 12 fitted to the flange 7 in the axial direction of the main shaft 2. is slidably and non-rotatably guided. A ζ bevel gear 13 is provided in the franchise, and the bevel gear 13 meshes with a bevel gear 14 to which power is transmitted from a rotational drive system. It is also possible to transmit the power from this rotational drive system by using a worm and a worm wheel, or by meshing a pair of spur gears.

A bevel gear 14 is provided on an output shaft 16 which is an output system of the differential gear device 15, and an i which is an input system of the differential gear device 15 is provided.
-m input shaft 17 is driven by a circumferential feed drive motor 18. A bevel gear 19 provided on the input shaft 17 and a bevel gear 20 meshing with the bevel gear 19 are a system for rotationally driving a table to which a workpiece (not shown) is attached, and are interlocked from the input shaft 17 side to form an indexing gear device. The table is usually driven by a worm and a worm wheel. Incidentally, in a CNC machine, the spindle 2 and the table are electrically controlled to rotate synchronously, so the above-mentioned interlocking is not necessary. A gear portion 21a is formed in a planetary gear support case 21, which is a planetary gear member that supports the planetary gears 15a of the differential gear device 15.

A crank pin 22 is attached to the upper end of the connecting rod 4, and the crank pin 22 is supported by a face plate 24 corresponding to a crank arm of a crankshaft 23 so as to be movable in the radial direction. A female thread is formed at the end of the crank pin 22, and the female thread is screwed into a feed screw 25 provided on the face plate 24. A pulley 26 is provided on the crankshaft 23, and power from a main motor 29 is transmitted to the pulley 26 via a belt 27 and a pulley 28. By operating the feed screw 25, the crank pin 22 moves in the radial direction on the face plate 24, the amount of eccentricity is adjusted, and the stroke length of the tool 1 is adjusted. When the vertical motion of the tool 1 is given by crank motion, the speed of the vertical motion draws a sine curve.

On the other hand, a face plate 30 is provided at the other end of the crankshaft 23,
A crank pin 32 is supported by the face plate 30 via a feed screw 31 so as to be freely movable in the radial direction. crank pin 32
One end of a connecting rod 33 is attached to , and a rack shaft 35 is supported at the other end of the connecting rod 33 via a pin 34 . The rack shaft 35 meshes with a pinion 38 of a shaft 37 provided with a gear 36 at one end, and the gear 36 meshes with the gear portion 21a of the planetary gear support case 21 described above. That is, by adjusting the rack 31, the moving stroke length of the rack shaft 35 is adjusted, the amount of rotation of the planetary gear support case 21 via the pinion 38 and the gear 36 is adjusted, and the face plate 30° feed screw 31 is adjusted. ．． Crank pin 32. Connecting rod 33. Pin 34. Rack shaft 35° pinion 38. Axis 3
7 and the gear 36 constitute a crank mechanism. The rotational speed of the planetary gear support case 21 also draws a sine curve similarly to the vertical movement speed of the tool 1.

In the above embodiment, the male shape 11 is fixed to the main shaft 2, but it is also possible to integrally form the male shape 11 on the main shaft 2 since there is no need to replace the male shape 11 when changing the helical angle. .

Next, the operation of the above configuration will be explained.

For the vertical movement Z of the tool 1, the pulley 28 is moved by the main motor 29.
, the rotation is transmitted to the crankshaft 23 via the belt 27 and the pulley 26, and the connecting rod 4, the spherical bearing 5, and the male type 11 are rotated with a stroke length that is twice the eccentricity of the crank pin 22 with respect to the center of rotation of the crankshaft 23. This is given by the main shaft 2 moving up and down via the . Feed screw 25
4! By doing so, the crank pin 22 moves in the radial direction on the face plate 24, the amount of eccentricity is adjusted, and the stroke length of the tool 1 is adjusted.

The rotational motion of the tool 1 is given by the rotation being transmitted to the flange 7 via a differential gear W15 and a bevel gear 14.degree.

When the planetary motion of the planetary gear 15a of the differential gear device 15 is stopped, the input shaft 17 and the output shaft 16 rotate at the same time, and the main shaft 2
moves up and down reciprocally along the female shape 12 while rotating in synchronization with the rotation of the rotating shaft for supporting the workpiece. Therefore, in this case, both gears are machined using a pinion cutter for straight teeth. To stop the planetary motion of the differential gear 15, the feed screw 31 is operated to move the crank pin 32 to the center of rotation of the face plate 30 so that the rack shaft 35 does not move.

When the crank pin 32 is made eccentric from the center of rotation of the face plate 30 by operating the feed screw 31, the rack shaft 35 moves up and down via the connecting rod 33 and pin 34 as the crankshaft 23 rotates. pinion 3
8. Planetary gear support case 21 via shaft 37 and gear 36
rotational force is transmitted to. When a rotational force is applied to the planetary gear support case 21, the output shaft 16 rotates due to the rotation of the input shaft 17 and the rotational force of the planetary gear support case 21. Therefore, the main shaft 2 rotates due to the rotation of the rotating shaft for supporting the workpiece. On the other hand, it reciprocates while rotating with a certain amount of twist. The amount of torsion can be adjusted as desired by adjusting the amount of eccentricity of the crank pin 32, and if the eccentric direction of the crank pin 32 is set to the opposite side, torsional rotation in the opposite direction can be obtained. Therefore, by arbitrarily adjusting the amount and direction of eccentricity of the crank pin 32, various torsional rotations can be given to the main shaft 2, and it is possible to process helical gears having any amount and direction of twist. You can do it.

The crank mechanism that moves the main shaft 2 up and down and the crank mechanism that rotates the planetary gear support case 21 are powered by the same crankshaft 23, so the vertical movement speed of the main shaft 2 and the crank mechanism that rotates the planetary gear support case 21 are The rotational speed should draw a sine curve, and the same torsional rotation as when using a helical guide should be given at any position in the vertical direction of the main shaft 2.

<Effects of the Invention> Since the gear shaper unspecified lead generating device of the present invention can adjust the helical angle steplessly,
It is possible to process multiple types of helical gears with different helical angles without replacing the guide member, eliminating the need for helical guides that are difficult to manufacture and expensive.

As a result, there are fewer restrictions on the design of the helical gear, and the processing setup change time is shortened, leading to improved production efficiency.

[Brief explanation of drawings]

FIG. 1 is a schematic configuration diagram of an unspecified lead generating device for a gear shaper according to an embodiment of the present invention, FIG. 2 is a cross-sectional side view of a helical guide mechanism, and FIG. 3 is a perspective view of a male helical guide. FIG. 4 is a schematic structural diagram showing the meshing state of the worm shaft and the worm wheel. The symbols in the figure are: 2 is the main shaft, 11 is the male type, 12 is the female type, 15 is the differential gear device, 16 is the output shaft, 17 is the input shaft, 18 is the circumferential feed motor, and 21 is the planetary gear support. Case, 23 is a crankshaft, 29 is a main motor, 30 is a face plate, 31 is a feed screw, 32
3 is a crank pin, 33 is a connecting rod, 34 is a pin, 35 is a rack shaft, 38 is a pinion, and 36 is a gear.

Claims (1)

[Claims] This is an unspecified lead generation device for a gear shaper, which is equipped with a cutter main shaft that reciprocates in the axial direction via a crank member while rotating with a rotation center axis extending in the same direction as the rotation center axis of a rotation shaft for supporting a workpiece. A guide member which cannot rotate with respect to the cutter main shaft and is slidable relative to the cutter main shaft in the axial direction is provided on the cutter main shaft, and an output system of a differential gear device in which an input system and an output system are connected via a planetary gear member is provided. In addition to being connected to the guide member, the input system of the differential gear device is connected to the rotational drive system of the cutter main shaft, and the crank member is optionally powered by the crank member in order to add lead generation rotation to the output system. A device for generating an unspecified lead of a gear shaper, which is connected to the planetary gear member side of the differential gear device through a crank mechanism capable of transmitting a signal to the planetary gear member.