JPS62124820A - Generating device for unspecified lead of gear shaper - Google Patents

Abstract

PURPOSE:To eliminate the necessity for using a helical guide and to perform machining of plural kinds of helical gears having a different helical angle in good production efficiency. CONSTITUTION:If a turning effect of a motor 18 is applied to a planet gear case 21, a main spindle 2 reciprocates while it rotates with a fixed twist amount for rotation of a work, and the work is cut by a tool 1. The twist amount is adjusted by selecting a number of teeth in a change gear device 33, and various twist rotations can be given to the main spindle 2 by meshing an idle gear with the device 33. A vertical movement is given to the main spindle 2 from a motor 29 through a male fitting 11. Accordingly, a helical angle can be steplessly adjusted, and plural kinds of helical gears of different helical angle can be cut with no necessity for a helical guide.

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 attached is movable back and forth in the axial direction and rotatable using a hydrostatic pressure bearing 3. It is guided and reciprocated in the axial direction via a spherical bearing 5 by a connecting rod 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 is 8! as shown in FIG. It meshes with a worm 10 provided on the machine side. The flange 7 is rotated through a worm wheel 9 by the rotation of the worm 10, and is driven to rotate synchronously with the helical gear, which is a workpiece, during gear cutting. In this case, the worm 10 is fixed in the axial direction. Here, there is a relationship between the lead length of the helical guide and the pitch circle diameter d of the gear cutting tool 1 as shown in the following equation.

π= dop= L-ψ...(1)
In addition, ψ is the helix angle of the gear cutting tool 1, m is the tooth normal module of the gear cutting tool 1, and 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 d. P is limited to a certain range and when 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-mentioned circumstances, and provides a gear shaper generating device for a gear shaper that can steplessly adjust a helical angle. The purpose of this invention is to make it possible to process a plurality of different types of helical gears, to eliminate the need for helical guides that are difficult and expensive to manufacture, and to improve production efficiency by shortening the setup change time for machining.

Means for Solving the Problems〉 The structure of the present invention for achieving the above object is to rotate in the axial direction with a rotation center axis extending in the same direction as the rotation center axis of the rotation shaft for supporting the workpiece. An unspecified lead generation device for a gear shaper equipped with a reciprocating cutter main shaft, wherein a guide member that 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 The input system and the output system are connected by connecting the output system of the differential gear device to the guide member, and connecting the input system of the differential gear device to the rotational drive system of the cutter main shaft, Connect the first gear mechanism to the planetary gear member of the device,
A cylindrical rank is formed on the cutter main shaft, a second gear mechanism is meshed with the cylindrical rack, and a replacement gear member capable of arbitrarily transmitting the power of the second gear mechanism is interposed so as to be connected to the first gear mechanism. It is characterized by being formed by connecting a second gear mechanism.

<Operation> When the power of the second gear mechanism associated with the axial reciprocating motion of the cutter main shaft 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 cutter main shaft receives rotational drive. The power from the system is directly transmitted through the guide member, and the cutter main shaft rotates and reciprocates in synchronization with the rotation of the rotating shaft for supporting the workpiece, and is applied to machining gears with no helix angle. When the power of the second gear mechanism is transmitted via the planetary gear member or the gear member, the output system of the differential gear device rotates with the power of the second gear mechanism added, and the second gear is transmitted to the cutter main shaft. The power from the rotational drive system to which the power of the mechanism is added is transmitted through the guide member, and the cutter main shaft rotates and reciprocates with a fixed amount of torsion relative to the rotation of the rotating shaft for supporting the workpiece, and adjusts the torsion angle. Applicable to gear processing. The amount and direction of twist of the cutter main shaft can be arbitrarily determined by adjusting the changeable gear member.

<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 a canter main axis, and a male type 111. It is slidably but non-rotatably guided in the axial direction of the main shaft 2 by a female shape 12 fitted onto the T flange 7 .

A bevel gear 13 is provided on the flange, 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.

An output shaft 16, which is the output system of the differential gear device 15, is provided with a bevel gear 14, and an input shaft 17, which is the input system of the differential gear device 15, is driven by a g-motor 18 for circumferential feeding. A bevel gear 19 provided on the input shaft 17 and a rake 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. In addition, in the CN C4jA machine, +, 1 spindle 2, table and 1. ? Since the rotations are electrically synchronously controlled, the above-mentioned interlocking is not necessary. Planetary gear 15a of differential gear device 15
A planetary gear support case 21 that is a planetary gear member that supports
A gear portion 21a is formed in the.

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.

Incidentally, the vertical movement of the main shaft 2 is not dependent on the above-mentioned crank mechanism, but it is also possible to use a driving means such as a hydraulic cylinder.

On the other hand, a cylindrical rack portion 30 is formed on the main shaft 2, and a pinion gear 31 is meshed with the cylindrical rack portion 30. One end of a shaft 32 is attached to the pinion gear 31, and the shaft 32
The other end is input to a replacement gear device 33, which is a replacement gear member, and the pinion gear 31 and shaft 32 constitute a second gear mechanism. Gear portion 21 of planetary gear support case 21
A gear 34 is meshed with a, and a shaft 35 is engaged with the gear 34.
One end of the is attached. The other end of the shaft 35 is input to the change gear device 33, the gear 34 and the shaft 35 constitute a first gear mechanism, and the first gear mechanism and the second gear mechanism are connected via the change gear device 33.

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.

The vertical movement of the tool 1 is performed by a main motor 29 using a pulley 28,
Rotation is transmitted to the crankshaft 23 via the belt 27 and pulley 26, and the connecting rod 4, spherical bearing 5, and 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 moving the main shaft 2 up and down through the shaft. 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. At this time, the pinion gear 31 meshing with the cylindrical rack part 30 rotates as the main shaft 2 moves up and down, and the rotation of the pinion gear 31 is input to the change gear device 33 via the shaft 32.

The rotational motion of the tool 1 is provided by the rotation being transmitted to the flange 7 by a circumferential feed nine-movement motor 18 via a differential gearing 15 and a bevel gear 14.

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 should be machined immediately using a pinion cutter for straight teeth. In order to stop the planetary motion of the differential gear device 15, the replacement gear device 3 is used to prevent the gear 34 from rotating.
Disengage the change gear 3 and transfer the power from the shaft 32 to the shaft 35.
I can't tell you.

When the replacement gears of the replacement gear device 33 are engaged, the main shaft 2
The rotation of the pinion gear 31 accompanying the vertical movement of the pinion gear 31 is transmitted to the gear 34 via the shaft 32, the replacement gear device 33, and the shaft 35, and the rotation of the gear 34 transmits rotational force to the planetary gear support case 21. 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 arbitrarily by appropriately selecting the number of teeth of the replacement gear in the replacement gear device 33, and also by preparing a set of idle gears in the replacement gear device 33 and meshing the idle gear with the replacement gear. For example, a torsional rotation in the opposite direction to that described above can be obtained.

Therefore, by appropriately selecting the number of teeth of the change gear of the change gear device 33 or by meshing the idle gear, the main shaft 2
Various torsional rotations can be applied to the helical gear, and helical gears having arbitrary twist amount and direction can be processed.

Since the rotation transmitted to the planetary gear support case 21 by the rotation of the gear 34 is directly linked to the vertical movement of the main shaft 2, it can be applied to any mechanism for vertical movement of the main shaft 2. Ru.

<Effects of the Invention> The gear shaper unspecified lead generating device of the present invention (
Since the helical angle can be adjusted steplessly, multiple types of helical gears with different helical angles can be processed without replacing the guide member, eliminating the need for expensive helical guides that are difficult to manufacture.

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 cylindrical rack portion, 31 is a pinion gear, 32 is a shaft, 33 is an exchange gear device, 34 is a gear, and 35 is a shaft. Patent applicant: Mitsubishi Heavy Industries, Ltd., acting agent

Claims (1)

[Claims] An unspecified lead generation device for a gear shaper, comprising a cutter main shaft that reciprocates in the axial direction 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, the cutter main shaft A guide member that is non-rotatable and movable relative to each other 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 connected to the guide member. At the same time, an input system of the differential gear device is connected to a rotational drive system of the cutter main shaft, a first gear mechanism is connected to a planetary gear member of the differential gear device, and a cylindrical rack is formed on the cutter main shaft. In addition, a second gear mechanism is meshed with the cylindrical rack, and the first gear mechanism and the second gear mechanism are connected by interposing a replacement gear member that can arbitrarily transmit the power of the second gear mechanism. Gear shaper unspecified lead generation device.