JPH0441106A - Tool rest driving device - Google Patents

Abstract

PURPOSE:To obtain a small-size and low-cost tool rest by selectively driving a rotary tool rest and a tool driving shaft using a single motor and considering the structures of a support and a tool driving system into a simple form. CONSTITUTION:A tool rest 21 is supported coaxially with a servo motor 2 by a fixed block 13 and a through shaft 34 is arranged coaxially therewith by penetrating the center of planetary gear reducer 6, to switch a power transmission passage from the servo motor 2 to the rotary tool rest 21 or to the tool driving shaft 24, as necessary, with a power transmission switching means 65 which is provided in the fixed block 5. In addition, the tool driving shaft 24 is arranged coaxially with an output shaft 3 and the tool rest 21 and combined with the through shaft 34 which penetrates the center of the planetary gear reducer 6, so that the planetary gear reducer 6 and the power transmission switching means 65 can be arranged around an axial line of the rotary tool rest 21 in a compact form because a tool rest driving input shaft 8 and a ring element 9 as the input and output shafts of the planetary gear reducer 6 are coaxial, to make the structures of a support and a rotary tool driving system simple.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a tool post drive device that drives a rotary tool post, and more specifically, to a tool post drive device that drives a rotary tool post and a drive shaft of a rotary tool supported by the tool post. The present invention relates to a tool post drive device that is downsized by being selectively driven by a single prime mover.

[Conventional technology]

Conventionally, as a machine tool having a rotary tool post, for example, Nc
Turret drives for tlj urns are known.

This device is equipped with a drive means including first and second prime movers for driving a rotary tool rest and a tool drive shaft, and a support thereof, and the rotary tool rest supporting a plurality of tools is driven by the first prime mover. While the rotary tool drive shaft provided in the rotary tool rest is driven by the second prime mover, the rotary tool drive shaft is provided in the rotary tool rest. Further, the first prime mover is connected to the rotary tool post via, for example, a parallel shaft gear type reducer, and the second prime mover is connected to the rotary tool drive shaft via a transmission means such as a pulley and a belt. .

[Problem to be solved by the invention]

However, in such a conventional tool post device, the first and second prime movers are used to index the rotation of the rotary tool post and drive the rotary tool, so the installation space for both prime movers is limited. Not only does the device become large because of the need to ensure the same, but the support structure to which the reducer and tool drive shaft are attached and the structure of the rotary tool drive system become complicated. Furthermore, although the rotational indexing of the rotary tool post and the driving of the rotary tool are not performed at the same time, separate prime movers are used for these drives, making it difficult to reduce the cost of the device. .

Therefore, the present invention enables a single prime mover to selectively drive a rotary tool post and a tool drive shaft, and also simplifies the support structure and tool drive system structure, thereby creating a small and low-cost tool post device. is intended to provide.

[Means to solve the problem]

In order to achieve the above object, the present invention provides a prime mover, a rotary tool rest that is disposed on the same axis as the prime mover, supports a plurality of tools, and is rotated by power from the prime mover; A support body consisting of a first block freely supported and a second block to which a prime mover is fixedly connected on the other side in the axial direction, a planetary gear reducer attached to the first block, and a rotary tool supported by a rotary tool rest. a power transmission shaft that passes through the center of the planetary gear reducer and extends coaxially with the prime mover and transmits power to the tool drive shaft; The present invention is characterized by comprising a power transmission switching means that is connected to either the planetary gear reducer or the power transmission shaft to switch the power transmission path.

[Effect]

In the present invention, the rotary tool rest is supported coaxially with the prime mover by the first block of the support, and the power transmission shaft is disposed coaxially with the planetary gear reducer by passing through the center thereof. The power transmission path from the prime mover to the rotary tool post or tool drive shaft is switched by the power transmission switching means provided in the 2-pro. Therefore, both the rotary tool post and tool drive shaft are selectively driven by a single prime mover, eliminating the need for two prime movers as in the past, and simplifying the structure of the support structure and rotary tool drive system. be done.

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

FIG. 1.2 is a diagram showing a first embodiment of a tool post drive device according to the present invention.

First, the configuration will be explained.

In Fig. 1.2, 1 is a support, 2 is a servo motor (prime mover) having an output shaft 3 and a case 4, and the case 4 of the servo motor 2 is the fixed block 5 (second block) of the support 1.
block). This fixed block 5 is
The supporting body 1 is physically connected to a fixed block 13 (first block) to which a planetary gear reducer 6 is attached, which will be described later, by a plurality of pins 7A and pins 7B. The planetary gear reducer 6 transfers power from the servo motor 2 to a cylindrical tool post drive input shaft 8 (
input shaft), decelerates it, and outputs it to the outside from an annular body 9 (output shaft) that is coaxial with the tool post drive input shaft 8.
Consists of R. The first stage reduction section 6F is composed of an input gear 11 formed on the base end side of the turret drive input shaft 8, and a gear 12 having a larger number of teeth than the input gear 11.

Further, the rear stage reduction section 6R includes a fixed block 13 that rotatably supports the annular body 9 via a bearing 10A and an IOB, and a pair of circular eccentric sections 15a and 15b having opposite phases, and a pair of bearings 14A and 14B, respectively. The three crankshafts 15 are supported by the fixed block 13 at equal intervals around the axis of the output shaft 3 via the three crankshafts 15, and are supported by the circular eccentric parts 15a, 15b of the crankshaft 15 via bearings 16A, 16B. , a pair of external gears 17A and 17B that revolve around the axis of the output shaft 3 with a phase difference of 180 degrees as the crankshaft 15 rotates;
Both external gears 17A, 1 have internal teeth 18a (pins) slightly more than the number of teeth of the external gears 17A, 17B in the annular body 9.
It is composed of an internal gear 18 and the like that mesh with the gear 7B. Then, the external gear 17A is driven by the input from the tool post drive input shaft 8.
, 17B revolve around the axis of the output shaft 3, the annular body 9 rotates according to the difference in the number of teeth between the external gears 17A, 17B and the internal gear 18.

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 a cutting tool and a drill (details are 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, the rotary tool rest 21 has a recess 21a inside, and the tool drive mechanism 22 is mounted on the fixed block 13 of the deceleration mechanism 6 so as to be located in the recess 21a of the rotary tool rest 21. . The tool drive mechanism 22 includes a fixing member 23 fixed to the fixing block 13 at a cross-sectional position (not shown), a tool drive shaft 24 coaxially supported by the fixing member 23 with the output shaft 3, and a bevel gear portion of the tool drive shaft 24. 24a
a bevel gear 25 supported by a support member 23 perpendicular to the output shaft so as to mesh with the output shaft; a spline shaft 26 spline-coupled within the bevel gear 25; and a thrust bearing 27.
The piston 28 is rotatably coupled to the spline shaft 26 via A, 27B, etc., and is slidably housed in the chamber 23c formed in the fixed member 23, and the spline shaft 26 and piston 28 are moved radially inward. A biasing spring 29 and a fixing block 5 so as to communicate with the chamber 23c.
．． 13 and the fixing member 23, and a plurality of bearings 31A, 31B, 32A, 32B.
Consists of etc.

Here, the tool drive shaft 24 is spline-coupled with a through shaft 34 (power transmission shaft) that is disposed coaxially with the output shaft 3 and passes through the center of the planetary gear reducer 6, and the rotation from this through shaft 34 is transferred to a bevel gear. 25 to a spline shaft 26, and when the piston 28 is pushed out radially outward against the biasing force of the spring 29, the spline shaft 26 It engages with any of the rotary tools T to drive it. Further, the through shaft 34 is coaxially supported by the output shaft 3 and the tool post drive input shaft 8 via a pair of bearings 35A and 35B,
A clutch mechanism 36 connects and disconnects the output shaft 3 between both bearings 35A and 35B. This clutch mechanism 36 is arranged in parallel within the fixed block 5, and includes a spur gear 37.38 that meshes with teeth 3a, 34a formed on the output shaft 3 and the through shaft 34, and a spur gear 37.38 that is arranged in the center of the spur gear 37.38 in an axial direction. A spline clutch shaft 39 is slidably fitted and spline-coupled to either one of the spur gears 37, 38 by the sliding action, and is compressed between the spur gear 37 and the clutch shaft 39 via a retainer member 40 and a pawl 41. and a spring 42 that biases the clutch shaft 39 to one side in the axial direction (right side in the figure), and a pressure that is provided so as to abut against the clutch shaft 39 via a pawl 43 and forms a part of the fluid pressure passage 30. It consists of a piston 45 that receives fluid pressure in the chamber 44 and moves the clutch shaft 39 to the other side in the axial direction (left side in the figure), and a pair of bearings 46 and 47 that pivotally support the spur gears 37 and 38. Then, due to the fluid pressure in the pressure chamber 44, the piston 45
When moves the clutch shaft 39 to the left in the figure,
Through the clutch shaft 39, the spur gear 37.38
are integrally engaged in the rotational direction, and a power transmission path from the output shaft 3 to the through shaft 34 and the tool drive shaft 24 is connected.

Further, the tool post drive input shaft 8 is connected to and disconnected from the output shaft 3 by a clutch mechanism 51 provided in the fixed block 5. This clutch mechanism 51 includes spur gears 52.53 arranged in parallel within the fixed block 5, and is fitted into the center of the spur gears 52.53 so as to be freely slidable in the axial direction. A spline clutch shaft 54 is spline-coupled to one end, and a spur gear 52 is connected to the other via a retainer member 55 and a ball 56.
and a spring 57 that is compressed between the clutch shaft 54 and biases the clutch shaft 54 in the axial direction;
A piston 59 is provided to abut against the clutch shaft 54 via a ball 58, and the piston 59 is biased by a spring force greater than that of the spring 57.
a spring 60 that moves the piston 59 to the other side in the axial direction, and a fluid pressure passage 6 defined between the piston 59 and the fixed block 5.
It consists of an annular pressure chamber 62 through which fluid pressure (for example, hydraulic pressure or pneumatic pressure) is introduced, and a pair of bearings 63 and 64 that pivotally support spur gears 52 and 53. When fluid pressure is introduced into the pressure chamber 62, the piston 59 moves so as to compress the subring 60, and the spur gear 52 and clutch shaft 54 become rotatable. The power transmission path is cut off. These clutch mechanisms 36 and 51 are provided in the fixed block 5 and interposed between the servo motor 2 and the turret drive input shaft 8 and tool drive shaft 24, and connect the servo motor 2 to the planetary gear reducer 6 or the tool drive shaft 24. A power transmission switching means 65 is connected to one of the tool drive shafts 24 to switch these power transmission paths.

On the other hand, a tooth clutch 70 capable of locking the rotation of the tool post drive input shaft 80 is provided on the tip side of the tool post drive input shaft 8.
3, an annular meshing member 72 formed with a tooth portion 72a that meshes with the tooth portion 71a of the fixed tooth member 71, and spline-coupled to the tool post drive input shaft 8 at the inner peripheral portion. , a piston 76 rotatably holding the meshing member 72 via thrust bearings 73, 74, and defining a pressure chamber 75 communicating with the fluid pressure passage 30 between the piston 76 and the fixed member 23; It consists of a plurality of disc springs 77 and the like that are compressed between the fixed block 13 and the piston 76 so that the fixed member 72 is spaced apart from the fixed tooth member 71. When fluid pressure is introduced into the pressure chamber 75 through the fluid pressure passage 30, the tooth clutch 70 engages the teeth 71a and 72a of the fixed tooth member 71 and the meshing member 72 to drive the tool post drive input shaft 8. Lock mechanically.

In addition, in FIG. 1, 81.82 is the fixed block 5.
There are two types of bearings mounted on the turret drive input shaft 8 that are attached to the turret drive input shaft 8 , and an encoder 83 that is provided close to the output shaft 3 and detects the rotation speed of the servo motor 2 . Further, the servo motor 2 is controlled by a control circuit (not shown) based on a detection signal of the encoder 83 according to a predetermined control program, and the fluid pressure passage 30 is controlled by a fluid pressure supply means (not shown) controlled by this control circuit. Pressurized air or pressure oil is appropriately supplied to the fluid pressure passage 61.

Next, the effect will be explained.

When the control circuit controls the operation of the servo motor 2 and the power transmission switching means 65 according to a predetermined program, the power transmission switching means 65 controls the output shaft 3.
and either the tool post drive input shaft 8 or the tool drive shaft 24 are coupled, and power is selectively transmitted from the servo motor 2 to the tool post drive input shaft 8 or the tool drive shaft 24.

For example, if fluid pressure is not supplied to the fluid pressure passage 30.61, the piston 7 of the tooth clutch 70
6 is displaced in the right direction in FIG. 1 by the spring force of the disc spring 77, so that the tool post drive shaft 8 can freely rotate. Further, the clutch shaft 39 of the clutch mechanism 36 is moved to the right in the figure by the biasing force of the spring 42, and the connection between the output shaft 3 and the tool drive shaft 24 is cut off, while the clutch shaft 54 of the clutch mechanism 51 is moved to the right in the figure. The output shaft 3 is moved to the left and the turret drive input shaft 8 is connected. Therefore, the turret drive input shaft 8 rotates together with the output shaft 3 at a predetermined rotational speed, and the rotational input of the turret drive input shaft 8 is transmitted to the deceleration mechanism 6.
The annular body 9 and the rotary tool rest 21 rotate together due to the deceleration output of the deceleration mechanism 6. When a predetermined rotary tool T (for example, a drill) becomes coaxial with the spline shaft 26 of the tool drive mechanism 22, the rotation of the servo motor 2 is stopped and the rotary tool rest 21 is stopped at a predetermined position. 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, and the servo motor 2 carries the load in the rotational direction that is received by the cutting edge. Do it like this.

The above-mentioned rotary tool 717) is in the selected state, the fluid pressure passage 30
．． When fluid pressure is supplied to the clutch shaft 39
moves to the left in the figure, the spur gears 37 and 38 are integrally connected, and the output shaft 3 and the tool drive shaft 24 are connected, while the spline shaft 26 is pushed out by the piston 28 against the spring force of the spring 29, and the spline shaft 26 is pushed out by the piston 28 against the force of the spring 29. shaft 2
6 engages with the rotary tool T. Furthermore, the fluid pressure supplied to the pressure chamber 62 causes the piston 59 to move to the right in the figure, and the clutch shaft 54 to move to the right in the figure, and the connection between the tool post drive input shaft 8 and the output shaft 3 is released. Furthermore, the tool post drive input shaft 8 is mechanically locked to the fixed block 13 by the tooth clutch 70.

In this state, when the servo motor 2 is driven, the tool drive mechanism 22 is moved through the through shaft 34 and the tool drive shaft 24.
Power is transmitted to the spline shaft 26, and the rotary tool T engaged with the spline shaft 26 is driven to rotate.

In this embodiment, the rotary tool rest 21 is supported coaxially with the servo motor 2 by the fixed block 13 serving as a support, and the through shaft 34 passes through the center of the planetary gear reducer 6 and is coaxial with these. The power transmission path from the servo motor 2 to the rotary tool rest 21 or the tool drive shaft 24 is appropriately switched by a power transmission switching means 65 provided in the fixed block 5. Therefore, both the rotary tool rest 21 and the tool drive shaft 24 are selectively driven by a single prime mover, and there is no need to provide two prime movers as in the conventional case. Furthermore, the tool drive shaft 24 is connected to the output shaft 3.
and a planetary gear reducer 6 coaxially arranged with the rotary tool rest 21.
The planetary gear reducer I6 and the power transmission switching means 65 are connected to the through shaft 34 passing through the center of the planetary gear reducer, and are also coaxial with the tool post drive input shaft 8 and the annular body 9, which are the input/output shafts of the planetary gear reducer. It becomes possible to arrange the rotary tool rest 21 compactly around the axis, and by simplifying the support structure and the rotary tool drive system, the tool rest drive device becomes smaller and the cost is reduced.

FIG. 3 is a diagram showing a second embodiment of the turret drive device according to the present invention, and in the figure, the same or equivalent structures as those in the first embodiment are denoted by the same reference numerals. The explanation will be omitted.

In FIG. 3, 101 is a support, 121 is a rotary tool rest, 122 is a tool drive mechanism, 124 is a tool drive shaft, 165
1 is a clutch mechanism (power transmission switching means), 170 is a tooth clutch, and the support body 101 is a fixed block 13 that rotatably supports the rotary tool rest 121 in one direction along the axis of the output shaft 3 of the servo motor 2, and the axis thereof. It consists of a fixed block 105 to which the servo motor 2 is fixedly connected on the other side in the direction. The rotary tool rest 121 supports a plurality of tools so as to protrude from the outer circumferential surface and the front surface, and is disposed coaxially with the servo motor 2, and also supports the output shaft of the planetary gear reducer 6 attached to the fixed block 13, that is, an annular body. 9, and is rotated by the deceleration output of the planetary gear reducer 6.

Further, a plurality of tool drive mechanisms 122 are provided corresponding to the number of rotary tools T mounted on the rotary tool rest 121, and one of the tool drive mechanisms 122 located at a predetermined index position is one of the plurality of tool drive mechanisms 122. Two rotary tools T are driven. Specifically, the tool drive shaft 124 has teeth 12 on the outer circumference.
Each tool drive mechanism 122 has a spur gear 125 that meshes with the teeth 124a of the tool drive shaft 124, and a spline connection in the spur gear 125 at one end. A spline shaft 126 that can be inserted and spline-coupled to a tool engaging member 131 (described later) at the other end, and a washer (or thrust bearing) 126a fitted to the spline shaft 126 and compressed between the tool engaging member 131. a spring 129 that biases the spline shaft 126 toward one end to release the spline connection between the spur gear 125 and the spline shaft 126;
It has a pair of tool engaging members 131 and 132 that engage with each other at bevel gear portions 131a and 132a. The spline shaft 126 is the rotary tool rest 12
It is arranged at the same radius position as one shirt eye 28 that is fitted into the support 13a of the fixed block 13 so as to be able to move in the axial direction around the axis of the rotary tool rest 121, A spline shirt l-126 of one tool drive mechanism 122 abuts against a shaft 128 via a ball 127 loosely fitted to one end thereof. Then, when this spline shaft 126 is moved to the other end side by the shaft 128, the spur gear 125 and tool engaging members 131 and 132 are connected to this spline shaft 12.
6, and power can be transmitted from the tool drive shaft 124 to the rotary tool T.

The clutch mechanism 165 is provided in the fixed block 105, which is the second block, and is a power transmission switching means that connects the servo motor 2 to either the planetary gear reducer 6 or the power transmission shaft 34 to switch the power transmission path. , specifically, are arranged coaxially within the fixed block 105, and the output shaft 3,
Teeth 3 formed on the turret drive input shaft 8 and the through shaft 34
Spur gear 136.13 that meshes with a, 8a, 34a
7.13B is spline-fitted to the center of the spur gear 136, and by axial movement, the spur gear 137 or 13
A spline clutch shaft 139 selectively spline-coupled to the shaft 128, a washer 140 fitted to the other end of the shaft 128, and a fixed block 105, and a ball 141 loosely fitted to the clutch shaft 139. A spring 142 that urges the clutch shaft 139 to one side in the axial direction (left side in the figure) by the intervening shaft 128 and a ball 143 are provided in the fixed block 105 so as to abut against the clutch shaft 39, and the fluid pressure passage 3
a piston 145 that receives fluid pressure in a pressure chamber 144 communicating with zero to move the clutch shaft 139 to the other side in the axial direction (right side in the figure), and a pair of bearings 146 to 148 that pivotally support spur gears 136 to 138. Consists of etc. Then, when fluid pressure is introduced into the pressure chamber 144, the piston 1
45, the clutch shaft 139 is moved to the right in the figure, and the spur gear 1 is moved through the clutch shaft 139.
36 and 137 are integrally engaged in the rotational direction, and the power transmission path from the output shaft 3 to the through shaft 34 and the tool drive shaft 24 is connected, and the shaft 128 is moved to the right in the figure by the clutch shaft 139. A spline shaft 126 is spline-coupled to the spur gear 125, and a power transmission path from the tool drive shaft 124 to the rotary tool T is connected. On the other hand, when the fluid pressure in the pressure chamber 144 is released, the spring 142 moves the clutch shaft 139 to the left in the figure, and the spur gears 136 and 138 are integrally engaged in the rotational direction via the clutch shirt eye 39. , a power transmission path from the output shaft 3 to the tool post drive input shaft 8 is connected.

Furthermore, the tooth clutch 170 includes a fixed tooth member 171 having a tooth portion 171a protruding toward the − side and attached to the fixed block 105, and a tooth portion 172a that meshes with the tooth portion 171a of the fixed tooth member 171. The fixed block 10 is fixed by an annular meshing member 172 that meshes with the teeth 8a of the tool post drive input shaft 8 at the outer peripheral teeth 172b and a rotation stopper 173.
A fluid pressure passage 1 is provided between the fixed shaft 174 which is fixed to the fixed block 105 and pivotally supports the meshing member 172, and the fixed block 105.
A piston 176 defining a pressure chamber 175 communicating with 61
The fixed block 105 and the meshing member 1
It is composed of a spring 177 and a thrust bearing 178 interposed between the tooth clutch 170 and the like.
When fluid pressure is introduced into the pressure chamber 175 through the fluid pressure passage 161, the fixed tooth member 171 and the meshing member 1
72 teeth 171a and 172a are engaged to mechanically lock the tool post drive input shaft 8.

In this embodiment, a fixed block 105 as a support is used.
The rotating tool rest 121 is supported coaxially with the servo motor 2 by the fixed block 13, and the through shaft 34
passes through the center of the planetary gear reducer 6 and is arranged coaxially therewith, and is connected from the servo motor 2 to the rotary tool rest 12 by a clutch mechanism 165 provided in the fixed block 105.
1 or the power transmission path to the tool drive shaft 124 is switched as appropriate. Therefore, the same effects as in the first embodiment can be obtained. Furthermore, the fluid pressure passage within the fixed block 13 can be eliminated, and the power transmission switching means can be made simpler.

FIG. 4 is a diagram showing a third embodiment of the tool post drive device according to the present invention, and in the figure, the same or equivalent structures as in the first and second embodiments are given the same reference numerals. The explanation will be omitted.

In FIG. 4, 201 is a support, 208 is a tool post drive input shaft, 221 is a rotary tool post, 222 is a tool drive mechanism,
224 is the tool drive shaft, 234 is the through shaft (power transmission shaft)
, 265 is a clutch mechanism (power transmission switching means), 270
is a two-scratch as a locking clutch mechanism,
The support body 201 includes a fixed block 13 that rotatably supports the rotary tool rest 221 on one side in the axial direction of the output shaft 3 of the servo motor 2, and a fixed block 205 to which the servo motor 2 is fixedly connected on the other side in the axial direction. Rotary turret 2
21 supports a plurality of tools at predetermined intervals so as to protrude from its front surface, and is disposed coaxially with the servo motor 2, and is connected to the output shaft of the planetary gear reducer 6 attached to the fixed block 13, that is, the annular body 9. The gears are fastened together and rotated by the reduction output of the planetary gear reducer 6.

Further, a plurality of tool drive mechanisms 222 are provided corresponding to the number of rotary tools T mounted on the rotary tool rest 221, and one of the tool drive mechanisms 222 located at a predetermined index position is one of the plurality of tool drive mechanisms 222. Two rotary tools T are driven. Specifically, the tool drive shaft 224 has teeth 2 on the outer circumference.
One end portion 23 of a through shaft 234 formed as a spur gear having a diameter 24a and pivotally supported at the center of the rotary tool rest 221.
4a, and each tool drive mechanism 2
22 includes a spur gear 225 that meshes with the teeth 224a of the tool drive shaft 224, a spline shaft 226 that is inserted into the spur gear 225 at one end so as to be spline-coupled, and that engages the rotary tool T at the other end;
The snap ring 226a fitted to the spur gear 22
The spring 229 is compressed between the spur gear 225 and the spline shaft 226 and urges the spline shaft 226 toward one end (left side in the figure) to release the spline connection between the spur gear 225 and the spline shaft 226. The spline shaft 226 is a shaft 22 that is inserted into the support portion 13a of the fixed block 13 so as to be movable in the axial direction around the axis of the rotary tool rest 221.
8 and is located at the same radius as the rotating tool rest 22.
At one predetermined index position, the spline shaft 226 of one of the tool drive mechanisms 222 abuts against the shaft 228 via a ball 227 loosely fitted to one end thereof. Further, the shaft 228 is urged to the left in the axial direction (left side in the figure) by a spring 231 \ that is compressed between the shaft 228 and the fixed block 205 , and abuts against the piston 233 . This piston 233 defines a fluid pressure chamber 232 communicating with the fluid pressure passage 230 between it and the fixed block 205, and when fluid pressure is supplied to the fluid pressure chamber 232, the piston 233 moves the shaft 228 and the spline shaft. 226 is moved to the right side in the figure, and the tool drive shaft 224
Power can be transmitted from the rotary tool T to the rotary tool T.

The clutch mechanism 265 is provided in the fixed block 205, which is a second block, and connects the servo motor 2 to either the turret drive input shaft 208 or the through shaft 234, which is the input shaft of the planetary gear reducer 6, to generate power. The transmission path can be switched, and specifically, the tooth section 208a formed on the end surface of the tool post drive input shaft 208 and the fixed block 205
．． a clutch operating chamber 237 formed in the clutch operating chamber 237; a piston 238 slidably housed within the clutch operating chamber 237;
A first coupling member 242 rotatably held by the piston 238 via a pair of thrust bearings 239A, 239B, a snap ring 240, and a stopper 241, and spline-coupled to the output shaft 3; teeth portions 243a on both sides;
243b is formed, and the second coupling member 243 is fixed to the first coupling member 242 so that the teeth 243a on the − side engage with the teeth 208a of the tool post drive input shaft 208, and the other end of the through shaft 234. The stopper member 2 is spline-coupled to the portion 234b so that the tooth portion 245a can mesh with the tooth portion 243b on the other side of the second coupling member 242.
The third coupling member 245 is fixed to the through shaft 234 via the third coupling member 244, and the second coupling member 243 is connected to the fixed block 205 and the piston 238 so that the piston 238 is biased in the direction in which the second coupling member 243 approaches the turret drive input shaft 208. It consists of a plurality of disc springs 246 contracted between the piston 238 and the fixed block 205, and a pressure chamber 247 defined between the piston 238 and the fixed block 205.

Furthermore, the tooth clutch 270 has a fixed tooth member 271 fixed to the fixed block 205 so that the teeth 271a formed on the negative side protrude into the clutch operating chamber 237, and a fixed tooth member 271 that is slidably inserted into the clutch operating chamber 237. The housed piston 272 is formed with a tooth portion 273a that can mesh with the tooth portion 271a of the fixed tooth member 271, and a spline portion 273b that is spline-coupled to the tool post drive input shaft 208, and a pair of thrust bearings 274A, 274B and a snap ring. 2
between the fixed block 205 and the piston 272 such that the annular meshing member 273 is rotatably held on the piston 272 via the ring 75, and the meshing member 273 urges the piston 272 in a direction away from the fixed tooth member 271. The pressure chamber 277 is defined between the piston 272 and the fixed block 205, and the like.

The fluid pressure passage 2 formed in the fixed block 205
When fluid pressure is introduced into the pressure chamber 247 through 30, the teeth 243b of the second coupling member 243 mesh with the teeth 245a of the third force spring 245, and power is transferred from the output shaft 3 to the tool drive shaft 224. The piston 2 is connected to the transmission path and receives the fluid pressure in the fluid pressure chamber 232.
33, the shaft 228 is moved to mesh with the spur gear 225, and a power transmission path from the tool drive shaft 224 to the rotary tool T is connected.

Also, at this time, the pressure chamber 27 is passed through the fluid pressure passage 230.
7 is supplied with fluid pressure, the fixed tooth member 271 and the meshing member 273 engage with each other, and the rotation of the tool post drive input shaft 208 is mechanically locked. On the other hand, when the fluid pressure in the pressure chambers 247 and 232 is released, the second coupling member 243
The tooth portion 243a is the tooth portion 208 of the tool post drive input shaft 208.
a, the power transmission path from the output shaft 3 to the planetary gear reducer 6 is connected, and the shaft 228 is moved to release the spline connection with the spur gear 225 by the spring 231, and rotates from the tool drive shaft 224. Tool T
The power transmission path to is cut off. Also, at this time, the fluid pressure in the pressure chamber 277 is released, the fixed tooth member 271 and the meshing member 273 are separated, and the turret drive input shaft 208 is unlocked.

Also in this embodiment, the fixed block 205 which is a support body
The rotary tool rest 221 is supported coaxially with the servo motor 2 by the fixed block 13, and the through shaft 23
4 passes through the center of the planetary gear reducer 6 and is arranged coaxially therewith, and a clutch mechanism 265 provided in the fixed block 205 connects the servo motor 2 to the rotary tool rest 2.
21 or the power transmission path to the tool drive shaft 224 is switched as appropriate. Therefore, the same effects as in the first and second embodiments can be obtained, and furthermore, the tool drive mechanism can be made simpler than in the second embodiment.

FIG. 5 is a diagram showing a fourth embodiment of the tool post drive device according to the present invention, and in the figure, the same or equivalent structures as in the first to third embodiments are given the same reference numerals. Therefore, the explanation will be omitted.

In FIG. 5, 301 is a support, 302 is a servo motor, 303 is an output shaft of the servo motor 302, 308 is a tool post drive input shaft, 321 is a rotary tool post, 334 is a through shaft (power transmission shaft), and 365 is a A clutch mechanism (power transmission switching means), 383 is a hollow encoder, 385 is a cutting oil supply mechanism, and the support body 301 is a fixed block 13 that rotatably supports the rotary tool rest 321 and the servo motor 302 are fixedly connected. It consists of block 305. Output shaft 303, turret drive input shaft 308, and through shaft 334
are each formed as a hollow shaft, and a supply vibrator 386 of a cutting oil supply mechanism 385 is disposed coaxially within both shafts 303 and 308. The rotary tool rest 321 has at least one cutting oil passage 38 extending radially outward from the center.
7 is formed, and a rotary valve 388 for distributing cutting oil is attached to the center thereof, and the rest is the same as the rotary tool rest 221 of the third embodiment.

The clutch mechanism 365 is provided in the fixed block 305 that is the second block, and connects the servo motor 302 to one of the turret drive input shaft 308 and the through shaft 334, which are the input shafts of the planetary gear reducer 6, to generate power. The transmission path can be switched, specifically, the turret drive input shaft 308
spline teeth 308a formed on the outer periphery of the end of the clutch actuating chamber 337 formed in the fixed block 305;
A piston 338 is slidably housed in a clutch operating chamber 337, a cylindrical first coupling member 339 is key-coupled to the output shaft 303, and a first coupling member 339 is spline-coupled to the first coupling member 339 at one end of the inner circumference. Spline teeth 30 of the tool post drive input shaft 308 at the tooth portion 343a and the other end of the inner circumference
A second coupling member 343 is formed with a tooth portion 343b that selectively couples to the piston 338, and is rotatably held on the piston 338 via a pair of thrust bearings 340A, 340B and a snap ring 341 at the outer periphery. The other end 33 of the through shaft 334 is secured by washers 344A and 344B.
4b, and the spline teeth 345a on the outer periphery are fixed to the second spline tooth 345a.
A third coupling member 345 that can mesh with the teeth 343a of the coupling member 343 is compressed between the fixed block 305 and the piston 338, and the second coupling member 343 meshes with the tool post drive input shaft 308. , and a plurality of disc springs 346 that bias the piston 338 so that the meshing member 273 separates from the fixed tooth member 271.
and a pressure chamber 347 defined between the piston 338 and the fixed block 305.

The fluid pressure passage 2 formed in the fixed block 305
When fluid pressure is introduced into the pressure chamber 347 through 30, the movement of the piston 338 causes the second coupling member 343 to
The tooth portion 343a of the third coupling member 345 is the tooth portion 343a of the third coupling member 345.
45a to connect the power transmission path from the output shaft 303 to the tool drive shaft 224, and to connect the fluid pressure chamber 2.
The shaft 228 connects the spline shaft 226 to the spur gear 22 by the piston 233 that receives the fluid pressure in the spline shaft 226.
5, and the power transmission path from the tool drive shaft 224 to the rotary tool T is connected. Further, at this time, the fixed tooth member 271 and the meshing member 273 mesh with each other, and the rotation of the tool post drive input shaft 208 is mechanically locked. On the other hand, when the fluid pressure in the pressure chambers 347 and 232 is released, the piston 338 is moved back by the disk spring 346, and the tooth portion 343b of the second coupling member 343 engages with the spline tooth 308a of the tool post drive input shaft 308. As a result, the power transmission path from the output shaft 303 to the planetary gear reducer 6 is connected, the power transmission path from the tool drive shaft 224 to the rotary tool T is cut off, and the turret drive input shaft 308 is also connected. The lock is now released.

The cutting oil supply mechanism 385 consists of the supply pipe 386, the cutting oil passage 387, and a rotary valve 388, and the rotary valve 388 communicates with the cutting oil passage 387 when the rotary tool rest 321 rotates to a predetermined index position (rotation direction The supply boat 389 is fixed to the supply pipe 386 by a rotation preventing member 390. Then, when the rotary tool rest 321 is rotationally indexed and the boat 389 communicates with the cutting oil passage 387, the cutting oil supplied through the supply pipe 386 from a supply point (not shown) passes through the cutting oil passage 387 to the cutting side (for example, , near the rotating tool T). Also, rotary valve 3
Seal rings 391A and 391B are attached to the outer periphery of 88 so as to sandwich the cutting oil passage 387 therebetween.

Also in this embodiment, the fixed block 305 which is a support body
The rotary tool rest 321 is supported coaxially with the servo motor 302 by the fixed block 13, and a through shaft 334 passes through the center of the planetary gear reducer 6 and is disposed coaxially therewith, and is provided in the fixed block 305. The power transmission path from the servo motor 302 to the rotary tool rest 321 or the tool drive shaft 224 is appropriately switched by the clutch mechanism 365.

Therefore, the same effects as in the first to third embodiments can be obtained, and furthermore, while maintaining the current space of the device,
A cutting oil supply mechanism 385 can be added.

〔effect〕

According to the present invention, the rotary tool post is supported coaxially with the prime mover by the first block of the support, and the tool drive shaft is disposed coaxially with the planetary gear reducer by penetrating the center thereof. Since the power transmission switching means provided in the second block switches the power transmission path from the prime mover to the rotary tool post or the tool drive shaft, a single prime mover can control both the rotary tool post and the tool drive shaft. It is possible to selectively drive, simplify the support structure and the structure of the rotary tool drive system, and provide a small, low-cost tool rest device.

[Brief explanation of drawings]

1.2 is a diagram showing a first embodiment of the tool post drive device according to the present invention, FIG. 1 is a plan sectional view thereof, FIG. 2 is a sectional view taken along the line A-A in FIG. 1, 3 is a plan sectional view showing a second embodiment of the tool post driving device according to the present invention, FIG. 4 is a plan sectional view showing a third embodiment of the tool post driving device according to the present invention, and FIG. The figure shows the fourth part of the turret drive device according to the present invention.
FIG. 2 is a plan sectional view showing an example. 2... Servo motor (prime mover), 5.105.
205.305...Fixed block (first block), 13...Fixed block (second block), 6.
...Planetary gear reducer, 8.208.308...Turret drive input shaft, 9
...... Annular body, 21.121.221.321 ... Rotary tool post, 24.124.224 ... Tool drive shaft, 34
．． 234.334...Through shaft, 65...
- Power transmission switching means, 165. 265. 365...Clutch mechanism (power transmission switching means) T...Rotary tool. agent

Claims (1)

[Claims] a prime mover, a rotary tool rest that is disposed on the same axis as the prime mover, supports a plurality of tools, and rotates by power from the prime mover; a first block that rotatably supports the rotary tool rest on one side in the axial direction; A support body consisting of a second block to which a prime mover is fixedly connected on the other side in the axial direction, a planetary gear reducer attached to the first block, a tool drive shaft that drives a rotary tool supported by a rotary tool post, and a planetary gear reducer. A power transmission shaft extends coaxially with the prime mover through the center of the gear reducer and transmits power to the tool drive shaft; A turret drive device comprising: a power transmission switching means that is connected to one of the two to switch a power transmission path.