JPH0441107A - Tool rest device - Google Patents

Abstract

PURPOSE:To obtain a small-size and low-cost tool rest by arranging an operating member and a clutch member for a tool driving unit at the same radial position to disconnect a power transmission passage from a tool driving shaft to a rotary tool with the axial movement of the operating member. CONSTITUTION:When fluid pressure is supplied to a fluid pressure passage 30, a piston 38 is moved to the right to combine the teeth 43a of the second coupling member 43 with the spline teeth 45a of the third coupling member 45 for connecting a power transmission passage from an output shaft 3 to a through shaft 34 and a tool driving gear 24. At this time, a shaft 28 is pushed out to the right against spring force of a spring 31 by the piston 32 which is subjected to fluid pressure in a pressure room 32 to combine the spline shaft 26 with a rotary tool T, so that a tool rest driving input shaft 8 is locked to a fixed block 13 by a tooth clutch 51. When the servo motor 2 is driven under such a state, power is transmitted to one tool unit 22 via the through shaft 34 and the tool driving gear 24 to rotationally drive the rotary tool T which is engaged with the spline shaft 26.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a tool post device, and more particularly to a tool post device that is miniaturized by simplifying the structure of a tool drive system that drives a rotary tool.

[Conventional technology]

Conventionally, as this type of tool post device, for example, a tool post device for an NC lathe is known. In this device, a rotary tool rest supporting a plurality of rotary tools is rotatably supported by a support body, and when the tool rest is indexed to a predetermined rotational position, one of the plurality of rotary tools is selected. Power transmission/cutoff operations are performed between one of the rotary tool drive shafts and a rotary tool drive shaft supported by the support body or the like.

[Problems to be Solved by the Invention] However, in such a conventional tool post device, as a means for operating power transmission/cutoff between the above-mentioned rotary tool and the rotary tool drive shaft, Since, for example, a hydraulic cylinder or the like is provided inside the rotary tool rest, there is a problem in that the structure becomes complicated.

Therefore, an object of the present invention is to simplify the mechanism for the above-mentioned power transmission/cutoff operation, and to provide a small and low-cost tool rest device.

[Means to solve the problem]

In order to achieve the above object, the present invention provides a rotary tool rest that supports a plurality of rotating tools, a support that rotatably supports the rotary tool rest, and an extension that extends parallel to the axis of the rotary tool rest through the support. There is an operating member that is movable in the axial direction, a tool drive shaft that is placed on the axis of the rotary tool post and inputs the power to drive the rotary tool, and a plurality of operating members that are located inside the rotary tool post corresponding to each rotary tool. a tool drive unit having axially movable clutch members, each of which is located on the same radius as the operating member, and drives the tool by moving one clutch member that abuts the operating member in the axial direction. This is characterized in that the power transmission path from the moving shaft to the rotary tool is connected and disconnected.

[Effect]

In the present invention, the operating member is provided to extend parallel to the rotary tool rest through the support body, and one of the plurality of tool drive units having a clutch member at the same radial position as the operating member is operable. By moving the clutch member that abuts the member in the axial direction, a power transmission path from the tool drive shaft disposed at the center of the rotary tool post to the rotary tool radially outward is connected/disconnected.

Therefore, the structure for connecting and disconnecting the power transmission path of the tool drive system is simplified. As a result, the cost of the tool rest device is reduced.

〔Example〕

Hereinafter, the present invention will be explained based on the drawings.

FIG. 1.2 is a diagram showing an embodiment of the tool rest device according to the present invention.

First, the configuration will be explained.

In Figure 1.2, l is the support, 2 is the hollow output shaft 3
and a servo motor (prime mover) having a case 4,
The case 4 of the servo motor 2 is the fixed block 5 of the support 1
(fixed part). This fixed block 5 is integrally connected to a fixed block 13, which will be described later, to which a planetary gear reducer 6 is attached by a plurality of bolts 7A, pins 7B, etc., and constitutes the support body 1. The planetary gear reducer 6 inputs the power from the servo motor 2 through a cylindrical tool post drive input shaft 8 provided coaxially with the output shaft 3 of the servo motor 2, reduces the power, and outputs the power from the servo motor 2 coaxially with the tool post drive input shaft 8. Annular body 9
It is designed to output to the outside from the front stage reduction section 6F.
and a rear stage reduction section 6R.

This front stage reduction section 6F includes an input gear 11 formed on the base end side of the tool post drive input shaft 8, and an input gear 11 formed on the base end side of the tool post drive input shaft 8.
The gear 12 has a larger number of teeth. Further, the rear stage reduction section 6R includes a fixed block 13 that rotatably supports the annular body 9 via the bearing 10A and IOB at the outer peripheral portion.
(support end portion) and a pair of opposite phase circular eccentric portions 15a, 1
5b and are pivotally supported on the fixed block 13 at equal intervals around the axis of the output shaft 3 via a pair of bearings 14A and 14B, respectively, and the supporting column 13a of the fixed block 13 has a free play. As well as being fitted, the bearings 16A, 16
Circular eccentric portions 15a, 15b of the crankshaft 15 via B
A pair of external gears 17A, 17B are supported in the annular body 9 and revolve around the axis of the output shaft 3 at 180 degrees different l6 phase as the crankshaft 15 rotates.
It is composed of an internal gear 18, etc., which has internal teeth 18a (pins) slightly more than the number of teeth of 7B, and meshes with both external gears 17A and 17B. When the external gears 17A, 17B revolve around the axis of the output shaft 3 due to the input to the turret drive input shaft 8, the annular body rotates according to the difference in the number of teeth between the external gears 17A, 17B and the internal gear 18. 9 rotates.

Reference numeral 21 denotes a rotary tool rest that is fastened to the annular body 9 by a plurality of bolts 20 and rotates integrally with the annular body 9 around the axis of the output shaft 3 . On the outer periphery of this rotary tool rest 21, there are a plurality of tools such as hides and drills (details not shown).
are attached at equal angular intervals, and a plurality of rotary tools T among these tools are rotatably supported by the rotary tool rest 21. Further, in the rotary tool rest 21, there are a plurality of tool drive units 22 corresponding to the number of rotary tools T mounted,
One tool drive shaft 24 that engages with these tool drive units 22 is provided, and one tool drive unit 22 located at a predetermined index position among the plurality of tool drive units 22 is driven by one tool drive shaft 24 by power from the tool drive shaft 24. It is adapted to drive a rotary tool T. Specifically, the tool drive shaft 24 is formed as a spur gear having teeth 24a on the outer periphery, is pivotally supported at the center of the rotary tool rest 21, is disposed coaxially with the output shaft 3, and is connected to the planetary gear reducer 6. Penetration shaft 3 passing through the center
Keyed to 4.

Each tool drive unit 22 includes a spur gear 25 that meshes with the teeth 24a of the tool drive shaft 24, and a spline shaft 26 that is inserted into the spur gear 25 at one end so as to be able to be splined and engaged with the rotary tool T at the other end. The clutch member) is compressed between the snap ring 26a fitted to the spline shaft 26 and the spur gear 25, and urges the spline shaft 26 toward one end (left side in the figure) to connect the spur gear 25 and the spline shaft 26. and a spring 29 for releasing the spline connection. The spline shaft 26 is arranged around the axis of the rotary tool rest 21 at the same radius as the shaft 28 (operating member) inserted into the support 13a of the fixed block 13 so as to be able to move in the axial direction. At a predetermined index position, the spline shaft 26 of one of the tool drive units 22 abuts against the shaft 28 via a ball 27 loosely fitted to one end thereof. Further, the shaft 28 is biased in one direction in the axial direction (to the left in the figure) by a spring 31 compressed between the shaft 28 and the fixed block 5, and abuts against the piston 33. This piston 33 defines a fluid pressure chamber 32 communicating with the fluid pressure passage 30 between it and the fixed block 5, and when fluid pressure is supplied to the fluid pressure chamber 32, this piston 33 causes the shaft 28 and The spline shaft 26 is moved to the right in the figure, and power can be transmitted from the tool drive shaft 24 to the rotary tool T.

The through shaft 34 has a pair of bearings 35A and 35B at the right end in the figure.
It is coaxially supported by the rotary tool rest 21 via the rotary tool rest 21, and is connected to and disconnected from the output shaft 3 by a clutch mechanism 36 at the left end in the figure. This clutch mechanism 36 is provided in the fixed block 5, and connects the servo motor 2 to one of the turret drive input shaft 8, which is the input shaft of the planetary gear reducer 6, or the through shaft 34 to switch the power transmission path. Specifically, the teeth 8a formed on the outer periphery of the end of the turret drive input shaft 8 on the servo motor 2 side, the clutch operating chamber 37 formed in the fixed block 5, and the clutch operating chamber 37 a piston 38 slidably housed therein, a first coupling member 42 spline-coupled to the output shaft 3, and a toothed portion 43a formed on the inner periphery of one end so as to be spline-coupled to the first coupling member 42. and a toothed portion 43b formed on the inner peripheral portion of the other end so as to mesh with the toothed portion 8a of the tool post drive input shaft 8,
A second coupling member 43 rotatably held on the piston 38 via a pair of thrust bearings 39A, -39B and a snap ring 41 on the outer periphery, and a toothed portion 45 on the outer periphery.
The third coupling member 45 is fixed to the through shaft 34 via a pair of stopper members 44 so that the second coupling member 43 can be engaged with the teeth 43a of the second coupling member 42, and the second coupling member 43 is moved to the left side in the figure. Fixed block 5 to move
and a plurality of disc springs 46 contracted between the piston 38 and the piston 38;
It consists of a pressure chamber 47 defined between the piston 38 and the fixed block 5, and the like.

Furthermore, a tooth clutch 51 that can lock the rotation of the tool post drive input shaft 8 is provided within the fixed block 5.
The tooth scratch 51 has teeth 52a formed on the negative side.
the fixed block 5 so that it protrudes into the clutch operating chamber 37.
a fixed tooth member 52 fixed to the fixed tooth member 52; and a tooth portion 53 that can mesh with the tooth portion 52a of the fixed tooth member 52 by movement of the piston 38.
a, and a spline portion 53b spline-coupled to the tool post drive input shaft 8. The spline portion 53b includes an annular meshing member 53 rotatably held on the piston 38 via a pair of thrust bearings 54 and a snap ring 55. and,
When fluid pressure is introduced into the pressure chamber 47 through the fluid pressure passage 30 formed in the fixed block 5, the teeth 43a of the second compression member 43 mesh with the teeth 45a of the third compression member 45 to produce an output. A power transmission path from the shaft 3 to the tool drive shaft 24 is connected, and the shaft 28 is moved to mesh with the spur gear 25 by the piston 33 which receives the fluid pressure in the fluid pressure chamber 32, and the rotary tool is transferred from the tool drive shaft 24. A power transmission path to T is connected.

Also, at this time, the movement of the piston 38 causes the fixed tooth member 52 and the meshing member 53 to mesh with each other, causing the turret drive input shaft 8
rotation is mechanically locked. On the other hand, when the fluid pressure in the pressure chambers 47 and 32 is released, the tooth portion 43b of the second coupling member 43 meshes with the tooth portion 8a of the tool post drive input shaft 8, and the output shaft 3 is connected to the planetary gear reducer. 6 is connected, the shaft 28 is moved by the spring 31 to release the spline connection with the spur gear 25, and the power transmission path from the tool drive shaft 24 to the rotary tool T is cut off. Further, at this time, the fixed tooth member 51 and the meshing member 53 are separated, and the lock of the tool post drive input shaft 8 is released.

On the other hand, in this embodiment, a cutting oil supply mechanism 60 is provided along the axis of the rotary tool rest 21.

This cutting oil supply mechanism 60 is connected to the case 4 of the servo motor 2.
A cutting oil supply vibro 1 (fixed pipe) is fixed to the rotary tool post 21 and coaxially arranged with the output shaft 3 and the tool post drive input shaft 8, and each tool drive unit 22 is connected from the center of the rotary tool post 21.
When the rotary tool rest 21 rotates to an arbitrary index position, it communicates with a predetermined cutting oil passage 62 corresponding to this index position. 62 and the position in the rotation direction match)
A distribution valve 65 having a supply port 63 and prevented from rotating between the supply vibro 1 and the supply vibro 1 by a rotation prevention member 64, and a pair of seal rings mounted on the outer periphery of the distribution valve 65 so as to sandwich the cutting oil passage 62. 66.67. Here, the supply vibro 1 includes one end portion 61a protruding from the rear end of the servo motor 2 to the outside, an intermediate portion 61b penetrating the output shaft 3 of the servo motor 2, and the other end portion 61c inserted into the rotary tool rest 21. The distribution valve 65 is connected to the other end 61C of the supply vibro 1.

Then, the rotary tool rest 21 is rotationally indexed, and due to the relative rotation between the rotary tool rest 21 and the distribution valve 65, the supply port 63 is at a fixed position and the cutting oil passage 62 whose rotational position matches the supply port 63.
When the two are in communication, cutting oil supplied from a cutting oil supply source (not shown) through the supply pipe 6e passes through this cutting oil passage 62 to the cutting side (for example, one rotary tool to which power is transmitted from the tool drive shaft 24). (near T).

In addition, in FIG. 1, 71.72 is the fixed block 5.
Two types of bearings are attached to 13 and pivotally support the tool post drive input shaft 8. Reference numeral 73 is an encoder that is provided close to the output shaft 3 and detects the rotational position and rotational speed of the servo motor 2. Further, the servo motor 2 is controlled by a control circuit (not shown) according to a predetermined control program based on the detection signal of the encoder 73, etc., and the fluid pressure passage 30 is controlled by a fluid pressure supply means (not shown) controlled by this control circuit. Pressurized air or oil is supplied as appropriate.

Next, the effect will be explained.

When the servo motor 2, the hydraulic pressure supply means, etc. are controlled by the control circuit in accordance with a predetermined cutting program, the clutch mechanism 36 connects the output shaft 3 and either the turret drive input shaft 8 or the through shaft 34. The servo motor 2 is connected to the tool post drive input shaft 8 or the tool drive shaft 2.
Power is selectively transmitted to 4.

For example, if fluid pressure is not supplied to the fluid pressure passage 30, the piston 38 is displaced to the left in FIG.
The output shaft 3 and the tool post drive input shaft 8 are integrated in the rotational direction through the servo motor 2 to the planetary gear reducer 6, and the power transmission path from the output shaft 3 to the through shaft 34 and the tool is connected. The power transmission path to the drive shaft 24 is cut off. Therefore, together with the output shaft 3, the turret drive input shaft 8
rotates at a predetermined rotation speed, the rotational input of the tool post drive input shaft 8 is decelerated by the planetary gear reducer 6, and the deceleration output of the planetary gear reducer 6 causes the annular body 9 and the rotary tool post 21 to be rotated.
rotates as one. Then, a predetermined rotary tool T (for example,
When the drill (drill) becomes coaxial with the spline shaft 26 of the tool drive unit 22, the rotation of the servo motor 2 is stopped and the rotary tool rest 21 is stopped. Note that when turning with a cutting tool or the like instead of a rotary tool, the servo motor 2 is servo-locked when the cutting tool reaches a predetermined index position.
The servo motor 2 is designed to bear the load in the rotational direction that is applied to the cutting edge.

When fluid pressure is supplied to the fluid pressure passage 30 in the selected state of the rotary tool T described above, the piston 38 moves to the right in the figure, and the tooth portion 43a of the second coupling member 43 and the third coupling member 45 The spline teeth 45a are combined to connect the power transmission path from the output shaft 3 to the through shaft 34 and the tool drive shaft 24. At this time, the piston 32 receiving the fluid pressure in the pressure chamber 32 pushes the shaft 28 to the right in the figure against the spring force of the spring 31, and the spline shaft 26 engages with the rotary tool T. Furthermore, at this time, the tool post drive input shaft 8 is mechanically locked to the fixed block 13 by the tooth clutch 51.

In this state, when the servo motor 2 is driven, power is transmitted to one tool drive unit 22 via the through shaft 34 and the tool drive shaft 24, and the spline shaft 26
The rotary tool T engaged with is driven to rotate. Here, in this embodiment, the planetary gear reducer 6 includes the external gears 17A,
17B is provided so as to fit loosely into the support portion 13a of the fixed block 13, and a shaft 28 is provided so as to extend in the axial direction of the rotary tool rest 21 through one of the support portions 13a. The spline shaft 26 of the unit 22 is provided at the same radial position as the shaft 28 so that it can abut against this shaft 28. One spline shaft 26 abutting the shaft 28 connects the power transmission path from the tool drive shaft 24 to the rotary tool T, while the return movement of the spline shaft 26 connects this power transmission path. Therefore, the support 1 to which the planetary gear reducer 6 is attached is simply constituted by the fixed block 13 having the support portion 13a, and the planetary gear reducer 6 and the tool drive shaft 24 are arranged around the central axis of the rotary tool rest 21. Compactly arranged. Furthermore, simply by moving the shaft 28 in the axial direction from the fixed block 5 side, the power transmission path from the tool drive shaft 24 to the rotary tool T can be connected or disconnected. There is no need to provide a cylinder or the like, and the structure for connecting and disconnecting is further simplified.

Furthermore, in this embodiment, both the rotary tool post 21 and the rotary tool T can be driven by a single servo motor 2, and the tool post drive input shaft 8 is an input shaft of the planetary gear reducer 6.
Since it is coaxial with the rotary tool rest 21, the clutch mechanism 36 can also be arranged compactly around the axis of the rotary tool rest 21, and the piston 33 and the spring 3
In combination with the fact that the shaft 28 can be easily driven using the fluid pressure that operates the clutch mechanism 36 by the simple driving means consisting of the following, it is possible to provide a small-sized, low-cost tool rest device.

〔effect〕

According to the present invention, the operating member penetrating the column body and the clutch members of the plurality of tool drive units are arranged at the same radial position, and the power transmission path from the tool drive shaft to the rotary tool is established by axial movement of the operating member. Since the power transmission path from the tool drive shaft to the rotary tool can be connected or disconnected simply by moving the operating member in the axial direction. Therefore, power transmission and
The structure for blocking can be further simplified.

As a result, it is possible to provide a small and low-cost tool rest device.

[Brief explanation of drawings]

1.2 is a diagram showing an embodiment of a tool rest device according to the present invention, FIG. 1 is a plan sectional view thereof, and FIG. 2 is a sectional view taken along the line A--A in FIG. 1. 1... Support body, 2... Servo motor (prime mover), 5...
・Fixed block (fixed part), 6... Planetary gear reducer, 13... Fixed block (support end), 13a.
...Strut portion, 17A, 17B...External gear, 18...
・Internal gear, 21...Rotary tool post, 22...Tool drive unit, 24...Tool drive shaft, 26...Spline shaft (clutch member) )
, 28... Shaft (operating member), T...
...Rotating tools.

Claims (1)

[Claims] A rotary tool rest that supports a plurality of rotating tools, a support that rotatably supports the rotary tool rest, and a support that extends parallel to the axis of the rotary tool rest through the support and is movable in the axial direction. An operating member, a tool drive shaft that is placed on the axis of the rotary tool post and inputs power to drive the rotary tool, and a plurality of tool drive shafts are provided in the rotary tool post corresponding to each rotary tool, each having the same radius as the operating member. a tool drive unit having an axially movable clutch member located above, the power transmission path from the tool drive drive shaft to the rotary tool is provided by moving one clutch member abutted against the operating member in the axial direction. A tool post device characterized in that the turret is connected and disconnected.