JPS6340655Y2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a debuff removal device, particularly to a debuff removal device that is effective when applied to a multi-tasking machine, that is, a numerically controlled lathe with a rotary tool.

In a numerically controlled lathe with a rotary tool, gears installed in the system that indexes and drives the main spindle in order to determine the position of the drill of the rotary tool attached to the main spindle are required to improve indexing accuracy, so there is no backlash. It is desirable to mesh. However, when turning is performed using a turning tool attached to the main spindle, the main spindle rotates at high speed, so if the gears provided in the system for indexing and driving the main spindle rotate at high speed while meshing without consistency, There is a risk of a seizure accident due to insufficient lubrication at the meshing portion.
Therefore, in the past, it was necessary to sacrifice the indexing accuracy of the rotary tool by providing a backlash that would not cause a seizure accident in the meshing portion of the gear.

The present invention was developed in view of the above circumstances, and is provided in the main spindle indexing drive system to enable drive without buckling when indexing the main spindle, and also to prevent meshing with buckling during turning. It is an object of the present invention to provide a data loss removal device that obtains the desired results.

In order to achieve this purpose, the present invention has developed a first gear that has consistent meshing with the gears on the output side.
A clutch gear and a second clutch gear are provided so as to be rotatable on the same axis as the clutch plate on the input side and both clutch gears can be relatively angularly displaceable, and the first clutch gear and the second clutch gear and a connecting means for removably connecting the clutch gear and the clutch plate, and the connecting means is configured to connect the first clutch gear and the second clutch gear to the clutch plate by the connecting means. This clutch is characterized by applying a force to the first clutch gear and the second clutch gear so that the teeth of both clutch gears assume positions out of phase with each other.

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below based on the drawings. FIG. 1 is a system diagram showing a drive system in a numerically controlled lathe with a rotary tool equipped with a debuff removal device 1 according to an embodiment of the present invention. Reference numeral 2 denotes a main shaft rotatably provided on the numerically controlled lathe with rotary tool. The main shaft 2 includes a gear 3 attached to the main shaft 2, a gear 4 that meshes with the gear 3, a gear 5 that rotates integrally with the gear 4, and a shaft 6 that is movable in the direction of arrow Z. It is indexed to a fixed position via gears 7 and 8 for switching the spindle rotation speed, a pulley 9, a belt 10, and a pulley 11, which can take a position in which it meshes with either gears 4 or 5 or does not mesh with either gears 4 and 5. It is rotatably driven by a motor 12 for possible turning drive.

FIG. 2 is a longitudinal cross-sectional view of the de-batch removal device 1;
FIG. 3 is a sectional view taken along the line -- in FIG. 2. In the debuff removal device 1, an input shaft 14 is rotatably supported within the casing 13.
is provided with a worm gear 15, and a worm 16 meshing with the worm gear 15 is connected to the servo motor 1.
It is directly connected to the output shaft of 7. In addition, the input shaft 14
rotatably supports a first clutch gear 18, and the first clutch gear 18 meshes with the output gear, that is, the gear 3, with backlash. Further, a second clutch gear 20 is fitted into a boss 19 provided on the first clutch gear 18 so as to be freely angularly displaceable relative to the first clutch gear 18. It has the same basic circle diameter as the clutch gear 18, and meshes with the gear 3 with consistency. Both clutch gears 18 and 20 have holes 2 at the same radius position.
1 and 22 are drilled. Reference numeral 23 is an engagement member that engages with both clutch gears 18 and 20 during assembly, and is a pin that regulates relative angular displacement between the two. That is, the large diameter portion 23a of the pin 23 fits into a hole 24 provided in the second clutch gear 20, and the small diameter portion 23b of the pin 23 fits into a long groove 25 provided in the first clutch gear 18. are doing. When both clutch gears 18, 20 are assembled in this way, both clutch gears 18, 20 have a state in which the phases of their respective teeth match, and a state in which the phase of each tooth matches that of both clutch gears 18, 20 and gear 3. It is possible to take a state of angular displacement corresponding to backlash in meshing.

A piston 26 is housed within the casing 13 so as to be movable parallel to the axis of the input shaft 14 . A rotary ring 27 is supported within the piston 26 so as to be rotatable and immovable in the axial direction relative to the piston 26 . A pin 28, which is a connecting member, is fixed to the rotary ring 27 at the same radial position as the hole 21, 22 of the clutch gears 18, 20, and the pin 28 has a tapered portion 28a at its tip. has. The pin 28 is connected to the input shaft 14
The clutch plate 29 is always fitted into the hole 30 of the clutch plate 29, and as the piston 26 moves, it passes through the hole 22 of the second clutch gear 20 and the hole 21 of the first clutch gear 18. A state in which the tapered portion 28a is fitted into the inside, and a state in which the tapered portion 28a is fitted inside the
can be pulled out from both holes 21 and 22.

Thus, the piston 26, the rotating ring 27 and the pin 28 are connected to the first clutch gear 18 and the second clutch gear 29.
The clutch gear 20 and the clutch plate 29 are detachably connected to each other by a connecting means 31.

Next, the operation in this embodiment will be explained. When turning with a numerically controlled lathe equipped with a rotary tool, the piston 26 is moved to the retracted position to disconnect the clutch plate 29 and the clutch gears 18, 20, and then the gear 7 or 8 and the gear 4 or 5 are engaged with each other, and the main shaft 2 is rotationally driven by the motor 12. FIG. 4 is a cross-sectional view of FIG. 3 in this state, FIG. 5 is a cross-sectional view of FIG. During turning, the gear 3 and main shaft 2 are rotationally driven by the motor 12, so as the gear 3 rotates in the direction of arrow A in FIG. 6, both clutch gears 18 and 20 perform driven rotation. At this time, the pin 28 is in a state where the clutch plate 29 and both clutch gears 18, 20 are disconnected, so the clutch plate 29, the rotating ring 27, etc. do not rotate. Also, at this time, since the angular displacement between the first clutch gear 18 and the second clutch gear 20 is not restricted by the pin 28, the meshing state between the gear 3 and the clutch gears 18 and 20 is as follows.
While the tooth surface 3a of the gear 3 is in contact with the tooth surfaces 18a, 20a of both clutch gears 18, 20, the tooth surface 3b of the gear 3 is in contact with the tooth surface 18 of both clutch gears 18, 20.
b, 20b, which causes a backlash b.

Next, when drilling is performed using a numerically controlled lathe with a rotary tool, the motor 12 is rotated.
The hole 22 of the second clutch gear 20 is indexed at a position corresponding to the predetermined index position of the pin 28. In this state, the piston 26 is hydraulically actuated to
8 into the hole 22 from the position indicated by the one-dot chain line in FIG. 5 to the position indicated by the two-dot chain line in the figure. When the pin 28 is further advanced, the tapered portion 28a of the pin 28 moves to the first position.
Since the hole 21 of the clutch gear 18 is pushed, the phases of the first clutch gear 18 and the second clutch gear 20 change. From figure 7 to figure 9 pin 2
8 shows the state when it reaches the final position, and FIG.
8 is a cross-sectional view of FIG. 3, and FIG. 9 is a cross-sectional view of both clutch gears 18, 20 and gear 3.
FIG. In this state, both the clutch gears 18 and 20 are integrally connected to the clutch plate 29 by the pin 28, and the tooth surface 18a of the clutch gear 18 is in contact with the tooth surface 3a of the gear 3, and the tooth surface 20b of the clutch gear 20 is in contact with the tooth surface 3a of the gear 3. Since the clutch gears 18 and 20 contact the tooth surface 3b of the gear 3, both clutch gears 18 and 20 mesh with the gear 3 without backlash. As a clutch mechanism installed in the turning drive system, the gears 7 and 8 are moved to the neutral position, and the servo motor 17 is rotated to rotate the worm 1.
6. Index the main shaft 2 via the worm gear 15, input shaft 14, clutch plate 29, pin 28, each clutch gear 18, 20, and gear 3. Drilling can be performed at this indexed position.

Since the present invention has the above configuration, it can bring about the following excellent practical effects.

In drilling or the like, the driving force on the input side can be transmitted between the clutch plate and both clutch gears and the input side gear without any backlash, so indexing can be performed with high precision. As a result, it has become possible to create a high-precision multi-tasking machine that automatically performs multiple operations such as turning and drilling in a small number of repeat operations with a single machine without the need for transportation, allowing for long-term unmanned machining. became possible.

By eliminating the backlash in the drive system including the backlash removal device, the output side can be indexed to the same position regardless of whether the input side rotates forward or backward, so high accuracy can be maintained in the indexing work. It is possible to perform shortcut indexing while Therefore, it is possible to improve efficiency by shortening working time.

When the output side gear of the backlash remover is driven to rotate at high speed by another drive system with the backlash remover turned off, each clutch gear is rotated by the output side gear in a meshed state with backlash. , there is no risk of seizure accidents due to high-speed rotation.

As both clutch gears 18, 20 and gear 3 wear out with use, both clutch gears 1
8, 20 and the gear 3 when the dimension of the backlash b increases, the piston 2
The amount of insertion of the pin 28 into the hole 21 of the clutch gear 18 is automatically increased based on the set pressure of a relief valve provided in the hydraulic system for moving the clutch gear 18.
In meshing the clutch gears 18, 20 with the gear 3, a predetermined forcing force can always be exerted to eliminate backlash.

It should be noted that the present invention is not limited to the explanation of the illustrated embodiments, and various modifications can be made within the scope of the claims of the utility model registration. In the example, in order to regulate the amount of phase shift between both clutch gears,
A tapered portion is provided at the tip to allow the pin to move freely toward both clutch gears, but by making a wedge instead of the pin movable toward both clutch gears, the amount of phase shift between both clutch gears can be similarly reduced. can be regulated.

[Brief explanation of the drawing]

The drawings show an embodiment of the present invention; FIG. 1 is a system diagram of a drive system in a numerically controlled lathe equipped with a rotary tool equipped with the deburring device of the present invention, FIG. 2 is a longitudinal cross-sectional view, and FIG. Figure - Sectional view, 4th
7 and 7 are cross-sectional views of FIG. 3, FIGS. 5 and 8 are cross-sectional views of FIG. 3, and FIGS. 6 and 9 are cross-sectional views of the first clutch gear and the second clutch gear. FIG. 3 is a front view showing a state of meshing with an output side gear. 1...Battery removal device, 2...Main shaft, 3
...Gear, 18...First clutch gear, 20...
...Second clutch gear, 26...Piston, 27
...Rotating ring, 28...Pin, 29...Clutch plate, 31...Connection means, b...Breakage.

Claims (1)

[Scope of utility model registration request] A first clutch gear and a second clutch gear, which are rotatably provided on the rotation shaft on the input side and mesh with one gear on the output side, respectively, and the first clutch gear and the second clutch gear are set relative to each other at a constant angle. an engaging member that is engaged with each other so as to be angularly displaceable; a clutch plate that is rotatably mounted on the axis of the rotation shaft on the input side in close proximity to the first and second clutch gears; The connecting member is movably provided in the clutch gear and is removably connected to a fitting hole formed in the first and second clutch gears to forcibly shift the phase of the first and second clutch gears. Features of the debatch removal device.