JPH0871848A - Device for converting linear motion into rotary motion and press rotating tool device using this device - Google Patents

Abstract

PURPOSE: To moderate the impact load produced to a device for converting linear motion, imparted by an impact means, into rotary motion by providing an impact absorbing member between the lower face of an internal thread member provided in the upper member of a body and the upper face in the lower member of the body. CONSTITUTION: When impact is applied to a pressing head member 21 by an impact element S to bring a plate keep 75 into contact with material W on a die D, impact load is applied to an external thread shaft member 29, but from this instant, an internal thread member 33 is pressed axially downward, and an impact absorbing member 41 bends, so that the external thread shaft member 29 also starts descending and starts rotating simultaneously. With the bending of the impact absorbing member 41, impact load at the time of the plate keep 7 coming in contact with the material W is absorbed and relaxed in large degree, which results in relaxing impact load to a device for converting linear motion, formed by the external thread shaft member 29 and the internal thread member 33, into rotary motion.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for converting a linear motion into a rotary motion and a rotary tool device for a press machine using the device, and more particularly to a tapping process, a drilling process or a reamer used for a press. The present invention relates to a rotary tool device for processing.

[0002]

2. Description of the Related Art As a conventional tapping device for a press machine related to the present invention, there is Japanese Utility Model Laid-Open No. 04-51323. This prior art includes: a tapping device main body mounted on an upper arm of a mold holder; a pressing head member that is provided so as to reciprocate in the axial direction and is pressed and driven in the axial direction by a pressing means of a press machine. A screw shaft member that is connected to the pressing head member and is given an axial movement, and that rotates by the axial movement by being screwed with a female screw member that is provided in the apparatus main body; A lead screw member that is rotatably supported by the apparatus body by screwing with a lead nut and that holds a tapping tool;
It is a tapping device for a press machine, which comprises an axial speed difference absorbing means for spline engaging the screw shaft member and the lead screw member so as to be capable of relative displacement in the axial direction.

[0003]

The conventional tapping device for a press described above has some problems due to the following reasons. In the tapping device for presses, when the punch head is hit with a press or a hitting element of the punch press, the tapping device descends and the plate holder at the bottom of the tapping device body comes into contact with the material, and the linear motion is changed to rotary motion. The linear movement of the screw shaft member is converted into a rotational movement by the means.

By the way, hit rate (the number of hits per minute) in a normal punching process of a punch press
Is used at about 300 times / minute, and the time required for the above-mentioned striker to move from top dead center to bottom dead center is about 0.1 seconds. If the stroke of the striker is 32 mm, this 32 mm will move at a speed of about 0.1 seconds. Therefore, when the above-mentioned conventional tapping device for a press machine is used in such a punch press, the plate retainer attached to the lower part of the main body collides with the material at a very high speed, and at the moment of the collision, the linear movement is performed. Therefore, a large impact load is applied to the means for changing the rotational movement, that is, the portion including the screw shaft member and the female screw member.

However, the screw shaft member hardly rotates at the moment when the plate retainer collides with the material, and immediately after that, the screw shaft member starts to rotate by the means for changing this linear motion into the rotary motion. The tapping process is started. In the conventional tapping device for press, there is a problem that the large impact load adversely affects the means for changing the linear motion into the rotary motion, that is, the screw shaft member and the female screw member, and shortens the life thereof. In addition, the impact load causes the plate retainer to make dents on the material, resulting in a decrease in product value.

By the way, in a normal punch press, the gap between the punch (male type) and the die (female type), that is, the so-called loose feed clearance (material feeding gap) is about 20 mm. Therefore, there is no problem in feeding a flat sheet metal material, but when performing tapping with a tapping die on a sheet metal material that has been subjected to forming processing such as bending,
The size of this feed clearance is important. That is, if this feed clearance becomes small, there is a problem that the material that has been subjected to the forming process with a large rise interferes with the punch (male type) and the die (female type) and cannot feed the material.

Further, when performing tapping with a tapping die, it is necessary to rotate the tap at least 7 times. In other words, 2 rotations in the process of biting the material of the tap,
This is because the screw machining process requires about 5 rotations. In order to give the tap 7 revolutions, if the means for changing the linear motion into a rotary motion, that is, if the lead of the screw of the screw shaft member and the female screw member is 4 mm, only the conversion process to the rotary motion causes punching. 28 mm of the stroke amount of the hitting element of the press will be used. If the lead of the screw is 3mm, this is 21mm and the difference is 7mm.
Becomes Since this 7 mm portion can be turned to the feed clearance, it is more advantageous to use a screw with a lead of 3 mm.

However, when the lead of the screw is 3 mm,
As shown in FIG. 6, it can be seen that the impact load is nearly three times that of the case where the lead is 4 mm. Of course, if the stroke speed of the striker is increased, the impact load also increases.
Therefore, in the conventional punch press or tapping device for a press, it is difficult to reduce the lead of this screw to increase the feed clearance.

The present invention has been made in view of the above problems, and an object thereof is to reduce the impact load generated in the conversion device in a device for converting a linear motion into a rotary motion by an impact load. The object of the present invention is to provide a device that converts linear motion with good durability into rotary motion.

It is another object of the present invention to provide a rotary tool device for a press machine which is capable of preventing a dent caused by a plate pressing on a processed product and having a sufficient feed clearance.

[0011]

In order to achieve the above object, a device for converting a linear motion into a rotary motion according to claim 1 is a device in which a linear motion is given by a pressing means. A main body composed of a member, a pressing head member axially reciprocally provided on an upper member of the main body, and driven to be pressed in the axial direction by the pressing means, and mounted inside the upper member of the main body, An urging means for urging the pressing head member in a direction opposite to the pressing direction by the pressing means; and an upper part of the main body, which is connected to the pressing head member and is given an axial movement through the pressing head member. A male screw shaft member that is rotated by the axial movement by screwing with a female screw member provided on the member;
A shock absorbing member provided between a lower surface of the female screw member provided in the upper member of the main body and an upper surface of the lower member of the main body, and for transmitting the rotation of the male screw shaft member to the driven shaft side. And a spline engagement shaft portion provided at the shaft end of the male screw shaft member.

According to a second aspect of the present invention, there is provided a device for converting a linear motion into a rotary motion, which is a device for converting a linear motion rotatably supported in a punch mounting hole of a press machine in an axial direction into a rotary motion. A main body composed of an upper member and a lower member, a pressing head member provided on the upper member of the main body so as to reciprocate in the axial direction, and pressed and driven in the axial direction by a pressing means of the press machine; A biasing means mounted inside the upper member of the main body, for generating a repulsive force in a direction opposite to the pressing direction of the pressing means of the pressing machine, and an axial line connected to the pressing head member. Provided in a mounting hole of a lower member of the main body, and a male screw shaft member which is given a directional movement and is rotated by axial movement by screwing with a female screw member provided in the upper member of the main body. A lead nut mounted on the lead nut support bodies, the lead screw member screwed to the lead nut with rotatably Mokeraru against the bush by with the body disposed on the lead nut support,
A plate retainer elastically mounted on a chuck protection ring member provided at the lower end of the lead nut support so as to reciprocate in the axial direction by a predetermined amount, a spline engagement shaft portion of the male screw shaft member, and the lead screw. Between the axial speed difference absorbing shaft connecting means formed by spline engagement with the spline engaging hole of the member, the lower surface of the female screw member provided in the upper member of the main body, and the upper surface in the lower member of the main body. And a shock absorbing member provided in the.

According to a third aspect of the present invention, a device for converting a linear movement into a rotational movement is the gas spring unit as the urging means in the first or second aspect.

Further, a device for converting linear motion into rotary motion according to a fourth aspect is the device according to the first or second aspect, wherein the shock absorbing member is a disc spring or a urethane rubber spring.

According to a fifth aspect of the present invention, in the apparatus for converting a linear movement into a rotational movement, the impact absorbing member is a disc spring or a urethane rubber spring.

According to a sixth aspect of the present invention, there is provided a rotary tool device for a press machine in which a linear movement is given by a pressing means, and a main body including a cylindrical upper member and a lower member, and an axial direction on the upper member of the main body. A pressing head member that is reciprocally provided and is pressed and driven in the axial direction by a pressing means of a press machine, and is mounted inside an upper member of the main body,
Biasing means for generating a repulsive force in a direction opposite to the pressing direction of the pressing head member by the pressing means of the press machine;
A male screw shaft member that is connected to the pressing head member and is given an axial movement from the pressing head member, and that is rotationally moved with the axial movement by screwing with a female screw member provided on an upper member of the main body, and a lower portion of the main body. A lead screw member that is rotatably supported by the main body by being screwed into a lead nut that is exchangeably fixed to the member, and that holds the rotating tool, and the male screw shaft member and the lead screw member are opposed to each other in the axial direction. An axial speed difference absorbing shaft connecting means for displaceably spline engaging, and a shock absorbing member provided between a lower surface of a female screw member provided in an upper member of the main body and an upper surface of a lower member of the main body. It is equipped with and.

According to a seventh aspect of the present invention, there is provided a rotary tool device for a press machine, which is axially reciprocally supported in a punch mounting hole of the press machine. The rotary tool device includes a cylindrical upper member and a lower member. A main body, a pressing head member which is provided on an upper member of the main body so as to reciprocate in the axial direction, and is pressed and driven in the axial direction by a pressing means of the press machine, and is mounted inside the upper member of the main body. ,
Biasing means for generating a repulsive force in a direction opposite to the pressing direction of the pressing head member by the pressing means of the press machine;
A male screw shaft member that is connected to the pressing head member and is given an axial movement from the pressing head member, and that is rotationally moved with the axial movement by screwing with a female screw member provided on an upper member of the main body, and a lower portion of the main body. A lead nut mounted on a lead nut support body provided in a mounting hole of a member and a lead nut supportable by a bush provided on the lead nut support body so as to be rotatable and axially slidable with respect to the main body, and the lead. A lead screw member screwed into the nut, and a chuck shaft supporting member of the tool chuck mounted on the hollow shaft portion of the lead screw member in the axial direction, and a chuck protection ring member provided at the lower end of the lead nut support. A plate retainer elastically mounted to be reciprocable in the axial direction by a predetermined amount, a spline engagement shaft portion of the male screw shaft member, and a spline engagement hole of the lead screw member are provided. Spline fitted provided, in which the shock absorbing member is provided between the upper surface of the lower member of the lower surface and the body of the female screw member provided in the upper member of the body.

According to an eighth aspect of the present invention, in the rotary tool device for a press machine according to the sixth or seventh aspect, the urging means is a gas spring unit.

Further, a rotary tool device for a press machine according to claim 9 is the rotary tool device according to claim 6 or 7, wherein the shock absorbing member is a disc spring or a urethane rubber spring.

Further, a rotary tool device for a press machine according to claim 10 is the rotary tool device according to claim 6, claim 7, claim 8 or claim 9, wherein the rotary tool is a tap, a reamer or a drill. .

A rotary tool device for a press machine according to an eleventh aspect of the present invention is a device for converting a linear motion into a rotary motion by a pressing means of a press machine, wherein a main body composed of a cylindrical upper member and a lower member, and A pressing head member that is provided in the upper member so as to be reciprocally movable in the axial direction and is driven to be pressed in the axial direction by the pressing means of the press machine, and is mounted inside the upper member of the main body, and the pressing head member is A biasing means for generating a repulsive force in a direction opposite to the pressing direction by the pressure means and a female screw member provided on the upper member of the main body, which is connected to the pressing head member and is given an axial movement therefrom. When the male screw shaft member that rotates in accordance with the axial movement is engaged with the lead nut that is fixedly exchangeably fixed to the lower member of the main body, the male screw shaft member is rotatably supported by the main body. Converts a linear motion into a rotary motion, which comprises a lead screw member for holding a rotary tool, and an axial speed difference absorbing shaft connecting means for spline-engaging the male screw shaft member and the lead screw member so as to be relatively displaceable in the axial direction. The punch mounting hole is reciprocally mounted in the punch mounting hole, and a die having a shock absorbing member mounted between the shock absorbing member holder and the material supporting member is mounted in the die mounting hole. is there. According to a twelfth aspect of the present invention, in the rotary tool device for a press machine according to the eleventh aspect, the impact absorbing member is urethane rubber or a disc spring.

Furthermore, a rotary tool device for a press machine according to claim 13 is the rotary tool device according to claim 11 or 12, wherein the rotary tool is a tap, a reamer or a drill.

[0023]

When the pressing head member is struck by the pressing means, for example, by a punch press or a hitting element of the press, the apparatus for converting linear motion into rotary motion according to claim 1 or 2 is provided. Since the shock absorbing member absorbs the shock load, the shock load applied to the male screw shaft member and the female screw member of the device that converts linear motion into rotary motion is mitigated.

By using the device for converting the linear motion of claim 3 into a rotary motion, an appropriate mounting load is applied to the urging means in addition to the action of claim 1 or claim 2. Moreover, the spring constant can be reduced.

Further, by adopting a device for converting linear motion into rotary motion as in claim 4, in addition to the action of claim 1 or claim 2, an appropriate load can be applied to the shock absorbing member with a short stroke. It is possible to give.

Further, by adopting the device for converting linear motion of claim 5 into rotary motion, in addition to the function of claim 3, it is possible to apply an appropriate load to the shock absorbing member with a short stroke. Become.

By using the rotary tool device for a press machine as claimed in claim 6 or claim 7, when the pressing head member is struck by a pressing means, for example, a punch press or a hitting element of the press, an impact is given. Since the absorbing member absorbs the impact load, the impact load applied to the male screw shaft member and the female screw member of the device that converts the linear motion into the rotary motion is mitigated.

According to the present invention, the rotary tool device for a press machine according to claim 8 is used.
In addition to the above action, an appropriate mounting load can be applied to the biasing means and the spring constant can be reduced.

Furthermore, by using the rotary tool device for a press machine as claimed in claim 9, in addition to the effect of claim 6 or claim 7, an appropriate load can be applied to the shock absorbing member with a short stroke. It will be possible.

According to a tenth aspect of the invention, in a rotary tool device for a press machine which uses a tap, a reamer or a drill as the rotary tool device, the same operation as that of the sixth, seventh, eighth or ninth claim is achieved. can get.

By using the rotary tool device for a press machine according to the eleventh aspect of the present invention, the impact load applied to the portion composed of the screw shaft member and the female screw member is alleviated, and
The impact load applied to the plate holder of the rotary tool device is also greatly reduced. Further, since the shock absorbing member is provided on the die side having a simple structure, the work of exchanging the shock absorbing member can be very simple.

Furthermore, by using the rotary tool device for a press machine according to the twelfth aspect, in addition to the action of the eleventh aspect, it becomes possible to apply an appropriate load to the impact absorbing member with a short stroke.

Furthermore, in the thirteenth aspect, in a rotary tool device for a press machine using a tap, a reamer or a drill as the rotary tool device, the same action as that of the eleventh or twelfth aspect can be obtained.

[0034]

Embodiments of the present invention will now be described in detail with reference to the drawings. Referring to FIG. 1, FIG. 1 shows a device 100 for converting a linear motion into a rotary motion and a rotary tool device 1 for a press machine using the device 100 according to the present embodiment, which is a top turret disk UT of a turret punch press. The state of being attached to the punch attachment hole PH is shown. In the embodiment of the rotary tool device 1 for a press machine, an example in which a tap is mounted as the rotary tool T is shown.

The rotary tool device 1 for a press machine has an upper member 3 and a lower member 5 which are fixedly connected to each other by a plurality of bolts 2, and a lead which is detachably fitted and mounted in a mounting hole 7 of the lower member 5. It has a tubular body 11 constituted by a nut support 9. The main body 11 is inserted into a punch mounting hole PH provided in an upper turret disc UT of the turret punch press, and is supported by a lifter spring SP at a fixed position with respect to the upper turret disc UT. The main body 11 is engaged with a key groove (not shown) provided in the lower member 5 and a punch key (not shown) provided in the upper turret disc UT to restrict rotation in the punch mounting hole PH. Has been done.

The upper member 3 is provided with a plurality of gas spring unit mounting holes 13 around the central axis of the main body 11. The gas spring unit mounting holes 1
The cylinder portion 17 of the gas spring unit 15 is attached to each of the three. This gas spring unit 1
The piston rod 19 of No. 5 projects upward, and the upper end of the piston rod 19 is connected and fixed to the pressing head member 21 by a plurality of bolts 22. The gas spring unit 15 generates a repulsive force that pushes back the pressing head member 21 in the direction opposite to the pressing direction of the hitting element S, which is the pressing means of the turret punch press, that is, in the upward direction in FIG. It is a means.

The gas spring unit 15 is one urging means for generating a repulsive force that pushes back the pressing head member 21 upward, and is not necessarily limited to the gas spring unit, and the piston rod 19 is not limited thereto.
It is also possible to apply a repulsive force that pushes back upward by using a compression coil spring or other elastic member.

As a characteristic of the gas spring, by setting the volume ratio of the piston rod to the volume of the cylinder 17 of the gas spring to be small, it is possible to reduce only the spring constant without changing the maximum load or the mounting load. . Therefore, if an appropriate gas spring is used as the urging means, there is an advantage that a dent is not generated in the material because the increase rate of the pressing force against the material is small even if the plate thickness of the processing material becomes slightly thick. Further, the coil spring causes damage due to fatigue in a short time when used under high stress, but the gas spring is more durable than the coil spring without damage due to fatigue when used under high stress.
On the other hand, the coil spring has an advantage that the price is lower than that of the gas spring.

The pressing head member 21 is reciprocally provided by the piston rod 19 in the axial direction with respect to the main body 11, that is, in the direction in which the hitting element S reciprocates in the vertical direction in FIG. , Has a flat upper surface 23 facing the hitting element S. In the pressing head member 21, an upper end portion of a male screw shaft member 29 composed of a ball screw shaft, a roller screw shaft or the like is formed by a thrust bearing 25 and a radial bearing 27.
It is rotatably connected about the axis of the shaft 9.

The male screw shaft member 29 has a male screw portion 31, and the male screw portion 31 is screwed to the female screw member 33 mounted on the upper member 3. The leads of the male screw portion 31 and the screw of the female screw member 33 are set to a relatively large value so as to smoothly convert the axial movement, that is, the linear movement of the male screw shaft member 29 into a rotational movement.

A key 35 is provided on the outer peripheral portion of the female screw member 33.
The key 35 is engaged with a key groove 37 formed on the inner circumference of the upper member 3 so as to be slidable in the vertical direction. A spacer 39 and a shock absorbing member 41 are provided between the lower surface of the female screw member 33 and the upper surface of the lower member 5.
And are provided. For the shock absorbing member 41, by using a disc spring or urethane spring having an appropriate size and shape according to the required performance,
An appropriate load can be applied to the shock absorbing member 41 with a short stroke.

Therefore, the female screw member 33 is restricted from rotating with respect to the upper member 3 by the engagement of the key 35 and the key groove 37, and is always pressed upward. However, if a downward force larger than the repulsive force of the shock absorbing member 41 is applied to the female screw member 33, only the bending amount of the shock absorbing member 41 can move downward.

The male screw shaft member 29 extends vertically through the female screw member 33 in the axial direction, and a spline engagement shaft portion 43 is provided in a lower region located inside the lower member 5. The spline engagement shaft portion of the present embodiment is formed on a spline shaft, and the rotational movement of the male screw shaft member 29 is spline engaged with a spline hole provided in a lead screw member 51 on the driven shaft side described later. Transmitted by. It is also possible to transmit the rotational movement of the male screw shaft member 29 by spline engaging the driven shaft side with the spline shaft and the rotary driving side with the spline hole.

The lead nut support 9 is a set screw 45.
The lead nut 47 is fixedly held by. The lead nut 47 has a screw hole 49 on the same axis as the male screw shaft member 29, and the lead male screw portion 53 of the lead screw member 51 is screwed into the screw hole 49. The screw lead of the screw hole 49 and the lead male screw portion 53 is set to the same value as the screw lead of the tap described later.

The lead screw member 51 extends vertically through the lead nut 47, and a spline member 55 is fixedly connected to the upper end portion thereof. The spline member 55 is
There is a spline hole 57, and the spline hole 57 is engaged with the spline engagement shaft portion 43 of the male screw shaft member 29 so as to be relatively movable in the axial direction.

Due to the above-described spline engagement that is relatively movable in the axial direction, there is a speed difference in the moving speed of the male screw shaft member 29 and the lead screw member 51 in the axial direction (vertical direction in FIG. 1). However, only the rotational movement of the male screw shaft member 29 can be transmitted to the lead screw member 51, which is the driven shaft, without any problem. That is, it is a shaft connecting means capable of absorbing the speed difference in the axial direction between the two shafts and transmitting the rotational motion or the rotational force.

The lead screw member 51 is rotatably supported in the bush 59 fitted in the lead nut support 9 and slidable in the axial direction.
A support shaft 67 of the tool chuck 65 is connected by a pin 63 so as to be movable in the axial direction by a predetermined amount. Further, the hollow shaft portion 61 is provided with a compression coil spring 69, and the compression coil spring 69 acts between the retaining pin 71 attached to the lead screw member 51 and the support shaft 67 so that the tool chuck 65 is shown in the drawing. Are pushing downwards. In the embodiment of FIG. 1, the tool chuck 65 is equipped with a tap which is a tapping tool.

A chuck protection ring member 73 and a plate holder 75 are attached to the lower end of the lead nut support 9 with bolts 77. Chuck protection ring member 73
Is fixed to the lower end portion of the lead nut support 9 by a bolt 77, while the plate retainer 75 can be displaced relative to the chuck protection ring member 73 by a predetermined amount in the axial direction. 1, which is biased downward in FIG. 1 by the compression coil spring 79.

The plate retainer 75 also serves as a piston operator of a cutting fluid supply pump (not shown) built in the main body 11, and when the plate retainer 75 moves in the axial direction toward the chuck protection ring member 73, As shown in FIG. 9 of the second embodiment described later, the cutting fluid in the cutting fluid tank 81 is sprayed from the cutting fluid injection nozzle 85 toward the tap through a cutting fluid passage (not shown). .

A lower turret disc LT is provided below the upper turret UT, and a die D is mounted in a die mounting hole DH of the lower turret disc LT.
The material W to be processed is placed on the die D. The die D has a hole through which the rotary tool T can pass.

FIG. 1 shows the initial state in which the striker S is in the raised position. When the striker S descends from this state, the striker S abuts the upper surface 23 of the pressing head member 21, and this is set in the axial direction. , Ie, downward in the figure. Then, first, the entire main body 11 is lowered with respect to the upper turret disc UT against the spring force of the lifter spring SP supporting the rotary tool device 1 for a press machine.

Further, when the pressing head member 21 is pressed, the plate pressing member 75 abuts on the upper surface of the material W on the die of the lower turret disk LT as shown in FIG. 2, and the main body 11 is further lowered. Then, the compression coil spring 79 bends and the chuck protection ring member 73
Comes into contact with the plate holder 75. At this moment, the plate holder 7
5, downward movement of the chuck protection ring member 73, the lead nut support 9, the lower member 5, the upper member 3, and the female screw member 33 is momentarily stopped.

At this time, the downward pressing force still acts on the male screw shaft member 29, but the male screw shaft member 29 does not rotate at that moment, and the male screw shaft member 29 stops descending at that moment. It is in the state of having done. Therefore, the male screw shaft member 2
An impact load will be applied to 9. However, from that moment, since the female screw member 33 is pressed in the downward axial direction and the impact absorbing member 41 bends, the male screw shaft member 29 also starts to descend and simultaneously starts to rotate. By bending the shock absorbing member 41 in this manner, the material W of the plate holder 75 is
The impact load at the time of contact with the
(See FIG. 3).

By the above operation, the impact load on the device for converting the linear motion of the male screw shaft member 29 and the female screw member 33 into the rotary motion is alleviated.

FIG. 5 shows the difference between the rotation resistance applied to the male screw shaft member in the conventional example without the impact absorbing means and the rotation resistance applied to the male screw shaft member in the case of the embodiment of the present invention. Compared to the case of the conventional example shown by the dotted line,
In the case of the embodiment of the present invention, the impact load is reduced to about 1/3, and the effect thereof will be well understood.

Further, a pump action is performed by the axial movement until the plate holder 75 contacts the chuck protection ring member 73, and the cutting fluid in the cutting fluid tank is ejected toward the tap.

When the pressing head member 21 is further pressed, the pressing head member 21 moves down against the upward repulsive force of the gas spring unit 15. With the further lowering of the pressing head member 21, the male screw shaft member 29 is screwed with the male screw shaft member 29 and the female screw member 33, and continues to descend while rotating at a degree determined by the screw lead. In this embodiment, this screw lead has a size of 3 mm. Therefore, the male screw shaft member 29
Moves axially by 3 mm per revolution.

For example, a punch press or a hitting element S of the press
Assuming that the stroke is 32 mm, the tap requires about 7 revolutions in the actual tapping process, and therefore, of the stroke 32 mm of the striker S, 21 mm (3 [3 [ mm / revolution] × 7 [revolution] = 21 mm) is used, and the remaining about 1
1 mm can be used as the feed clearance F.

The rotation of the male screw shaft member 29 is transmitted to the spline member 55 of the driven shaft by the spline engagement shaft portion 43, whereby the lead screw member 51 rotates. Since the lead screw member 51 is screwed into the lead nut 47, the lead screw member 51 can rotate and move in the axial direction at a degree determined by the screw lead, thereby tapping the tool chuck 65. While rotating, it descends and engraves a female screw in the prepared hole of the material W.

In this tapping process, the male screw shaft member 29 descends in the axial direction at a degree determined by the lead of the male screw portion 31, and in response to this, the lead screw member 51 causes the screw lead of the lead male screw portion 53 to move. That is, it descends with a degree determined by the same screw lead as the tap for tapping. by the way,
Since the lead of the male screw portion 31 is larger than the lead of the lead male screw portion 53, the male screw shaft member 2
9 rotates in the same direction as the lead screw member 51 at the same rotation speed, but descends at a higher speed than that in the axial direction.

Therefore, the amounts of axial movement of the male screw shaft member 29 and the lead screw member 51 are different from each other. Since the male screw shaft member 29 and the lead screw member 51 are axially connected to each other in the axial direction by spline engagement by the spline engagement shaft portion 43 and the spline hole 57 of the spline member 55, respectively. The male screw shaft member 29 and the lead screw member 51.
Is rotated while sliding in the axial direction at the spline engagement portion, and the axial movement and rotation of the two are performed without interfering with each other.

The tapping process is completed when the striker S descends to the lowest position as shown in FIG. Subsequently, the striker S starts to rise, and as the striker S rises, the pressing head member 21 moves upward with respect to the main body 11 due to the repulsive force of the gas spring unit 15. As a result, the male screw shaft member 29 is reversely rotated, all of the spline member 55 and the lead screw member 51 are reversely rotated, and the male screw shaft member 29 and the lead screw member 51 are respectively raised by their respective screw leads. The pressing head member 21 returns to the position shown in FIG. In this state, the tap has already been separated from the material, and the upper member 3 supported by the lifter spring SP further moves upward and returns to the initial state of FIG.

7 and 8, a drill DR is provided on the tool chuck 65 in the first embodiment of the rotary tool device for a press machine using the device 100 for converting linear motion into rotary motion according to this embodiment. Alternatively, an example in which a reamer R is attached is shown. FIG. 9 shows a second embodiment of the rotary tool device for a press machine using the device 100 for converting a linear motion into a rotary motion according to this embodiment. In FIGS. 7, 8 and 9, the same parts as those in the first embodiment described above are designated by the same reference numerals.

The main structure of the second embodiment shown in FIG. 9 is the same as that of the first embodiment described above, and the operation and effect thereof are also the same, so the description of the same parts will be omitted and a new one will be added. Only the structure and operation of the improved part will be described. In addition, the tool chuck 6 is used in the second embodiment.
5 shows a rotary tool device for a press machine with a tap attached.

Referring to FIG. 9, a cutting fluid tank 81 is attached to the side surface of the upper member 3, and the cutting fluid is contained therein. A cutting fluid nozzle 85 having a cutting fluid ejection port is provided in the vicinity of the tap, and the plate retainer 75 also serves as an actuator of a piston of a cutting fluid supply pump (not shown) built in the main body 11. By the movement of the plate holder 75 in the axial direction, the cutting fluid passes through a cutting fluid passage (not shown) and is jetted from the cutting fluid nozzle 85 to the tap.

Further, a ring-shaped elastic member 83 is provided between the chuck protection member 73 and the plate holder 75 so as to be expandable and contractible. In the embodiment, urethane rubber is used as the material of the elastic member 83. However, the elastic member is not limited to urethane rubber as long as it is an elastic member having characteristics similar to urethane rubber or an elastic member having higher performance.

By providing the elastic member 83 between the chuck protection member 73 and the plate retainer 75, the impact when the plate retainer 75 collides with the material W is further alleviated.

FIG. 10 shows a third rotary tool device for a press machine.
FIG. Referring now to FIG. 10, the rotary tool device for a press machine according to the third embodiment includes a device 200 for converting a linear motion into a rotary motion and a die 89. The rotary tool device 200 for a press machine and the die 89.
Is the punch mounting hole PH of the upper turret disc UT.
And the lower turret disc LT are coaxially mounted in the die mounting hole DH for use. In the embodiment of FIG. 10, the tool chuck 65 is equipped with a tap which is a tapping tool.

The device 200 for converting the linear motion into the rotary motion has the same structure as that of the rotary machine for press machine 1 shown in FIG. 1 except that the shock absorbing member 41 is omitted. Since it is exactly the same as the device 1, description of its configuration is omitted.

As described above, the device 200 for converting a linear motion into a rotary motion does not have a shock absorbing member, so that the die 89 side has this shock absorbing function.

The die 89 comprises a shock absorbing member holder 91, a material supporting member 93, a shock absorbing member 95 and the like. A plurality of shoulder screws 97 are provided on the upper portion of the shock absorbing member holder 91.
Is connected to the shock absorbing member holder 91 so as to be movable in the vertical axis direction, and the amount of vertical movement thereof is regulated by the length of the shaft portion 96 of the shoulder screw 97. A tool passage hole 99 through which the rotary tool T can pass is provided at the center of the material support member 93.

Further, the shock absorbing member holder 91 is provided with a shock absorbing member mounting seat 98, and the shock absorbing member mounting seat 98 and the material supporting member 93 are provided with an appropriate mounting load between the shock absorbing member mounting seat 98 and the material supporting member 93. The absorbing member 95 is attached. It is preferable to use an elastic body such as urethane rubber or a disc spring for the shock absorbing member 95. Further, the impact absorbing member mounting load is equal to or more than the total of the mounting load of the biasing means in the device 200 for converting the linear motion into the rotary motion and the rotation resistance of the male screw shaft member 29. It is appropriate to set.

The operation and action of the rotary tool device for a press machine according to the third embodiment will be described. When the striker S contacts the upper surface 23 of the pressing head member 21 and presses it in the axial direction, that is, in the downward direction in FIG. 10, the spring force of the lifter spring SP supporting the rotary tool device for the press machine. Against the main body 11
Is lowered with respect to the upper turret disc UT.

Further, when the pressing head member 21 is pressed by the striker S to lower the main body 11, the plate pressing member 75 comes into contact with the upper surface of the material W on the die 89.
Since the main body 11 is still pressed, the main body 11 is further lowered. However, since the plate retainer 75 is in contact with the upper surface of the material W, the compression coil spring 79 is bent and the chuck protection ring member 73 is in contact with the plate retainer 75.

Therefore, when the striker S further descends from this state, the pressing force of the striker S is applied to the shock absorbing member holder 91 and the material support member 93 through the gas spring unit 17, the main body 11 and the plate retainer 75. The impact absorbing member 95 mounted between the two is compressed until the material supporting member 93 comes into contact with the impact absorbing member holding body 91.

Shock absorbing member holder 91 and material supporting member 9
3, the striker S is still pressed against the pressing head member 21.
Since the pressing head member 21 is pressed, the pressing head member 21 is further lowered against the upward repulsive force of the gas spring unit 17. As the pressing head member 21 descends, the male screw shaft member 29 is given a downward linear motion, and the male screw shaft member 29 and the female screw member 33 are screwed to each other, so that the male screw shaft member 29 is determined by the screw lead. It comes down while rotating with.

Therefore, the rotation of the male screw shaft member 29 is transmitted to the spline member 55 of the driven shaft by the spline engagement shaft portion 43, whereby the lead screw member 51 rotates. The lead screw member 51 is the lead nut 4
Since the lead screw member 51 is screwed into the shaft 7, the lead screw member 51 moves in the axial direction while rotating with a degree determined by the screw lead.
The tap of the above will descend while rotating, and an internal thread will be carved in the prepared hole of the material W.

When the striker S is lowered to the lowest position, the tapping process is completed, and as the striker S is raised, the pressing head member 21 is moved upward by the repulsive force of the gas spring unit 15. Body 11
To move up against. As a result, the male screw shaft member 29 is reversely rotated, and accordingly, all of the spline member 55 and the lead screw member 51 are reversely rotated, so that the male screw shaft member 29 and the lead screw member 51 each have their respective screw leads. To rise.

When the pressing head member 21 returns to the initial state by the repulsive force of the gas spring unit 15, the main body 11 also returns to the original supporting position by the lifter spring SP. In the operation of the rotary tool device for a press machine according to the third embodiment, the impact load generated when the plate pressing member 75 abuts on the upper surface of the material W on the die 89 is caused by the impact absorbing member 95 provided on the die 89. By flexing, the first,
The absorption is relaxed as in the second embodiment.

In the rotary tool device for a press machine of the third embodiment, the impact absorbing member is provided only on the die 89 side, but it is provided on both the die 89 side and the device for converting linear motion into rotary motion. It may be provided.

[0081]

As can be understood from the above description, according to the invention of claim 1 or 2, when the pressing head member is hit by the pressing means, the shock absorbing member absorbs the shock load. Therefore, the impact load applied to the male screw shaft member and the female screw member of the device that converts linear motion into rotary motion is relaxed, and the life of the device that converts linear motion into rotary motion can be extended.

According to the invention of claim 3, claim 1
In addition to the effect obtained by the invention of claim 2, the spring constant can be reduced and the life of the biasing means can be extended without changing the mounting load of the biasing means.

Further, according to the invention of claim 4, in addition to the effect obtained by the invention of claim 3, since an appropriate load can be applied to the shock absorbing member with a short stroke, a compact linear motion can be rotated. It is possible to make a device that transforms into motion.

Furthermore, according to the invention of claim 5, in addition to the effect obtained by the invention of claim 3, since an appropriate load can be applied to the shock absorbing member with a short stroke, a compact linear motion can be achieved. It is possible to make a device that transforms into rotary motion.

According to the invention of claim 6 or 7,
When the pressing head member is struck by the pressing means, for example, a punch press or a hitting element of the press, the shock absorbing member absorbs the shock load, so that the shock load applied to the male screw shaft member and the female screw member is relaxed. , It is possible to extend the life of the device that converts linear motion to rotary motion,
In addition, no dent is formed on the material due to the pressing of the plate. Further, since the lead of the male screw member can be set small, the feed clearance can be increased. As a result, for example, even a material such as "cut and raised" and "louver" having a concavo-convex shape can be fed between the die and the plate holder without any obstacle.

Further, according to the invention of claim 8, in addition to the effect obtained in claim 6 or claim 7, the spring constant can be reduced without changing the mounting load of the biasing means. Even if the plate thickness changes, the change in the load applied to the plate retainer can be reduced. As a result, even if the plate thickness of the material is increased, it is possible to prevent dents due to the plate pressing.

Further, according to the invention of claim 9, in addition to the effect obtained in claim 6 or claim 7, an appropriate load can be applied to the shock absorbing member with a short stroke, so that it is compact. It is possible to fabricate the device.

Further, according to the invention of claim 10, in a rotary tool device for a press machine, which uses a tap, a reamer or a drill as the rotary tool device, the claim 6, claim 7, claim 8 or claim 9 The same effect as can be obtained.

According to the eleventh aspect of the present invention, the impact load applied to the portion composed of the screw shaft member and the female screw member is alleviated. In addition, since the impact load applied to the plate holder is greatly reduced, dents due to the plate holder are not generated. Further, since the shock absorbing member is provided on the die side having a simple structure, the work of exchanging the shock absorbing member can be very simple.

Further, according to the invention of claim 12, in addition to the effect obtained in claim 11, an appropriate load can be applied to the shock absorbing member with a short stroke, so that a compact die can be manufactured. You can

Further, according to the invention of claim 13, in a rotary tool device for a press machine which uses a tap, a reamer or a drill as a rotary tool device, the same effect as that of claim 11 or 12 can be obtained. it can.

[Brief description of drawings]

FIG. 1 is a view showing an embodiment of a device for converting a linear motion into a rotary motion and a rotary tool device for a press machine using the device according to the present invention.

FIG. 2 is an operation explanatory view of an embodiment of an apparatus for converting a linear motion into a rotary motion according to the present invention and a rotary tool device for a press machine using the device.

FIG. 3 is an operation explanatory diagram of an embodiment of an apparatus for converting a linear motion into a rotary motion according to the present invention and a rotary tool device for a press machine using the device.

FIG. 4 is an operation explanatory diagram of an embodiment of a device for converting a linear motion into a rotary motion and a rotary tool device for a press machine using the device according to the present invention.

FIG. 5 shows the relationship between the rotational resistance of the male screw member and the time in the conventional device in one embodiment of the device for converting a linear motion into a rotary motion and the rotary tool device for a press machine using the device according to the present invention. The figure shown in comparison with that of the case.

FIG. 6 is a view showing an example of a relationship between a rotational resistance applied to a male screw member of a lead of a tapping device for a press machine and a time when various leads or stroke speeds are changed.

FIG. 7 is a drawing of an embodiment in which a drill is attached to a tool chuck in a rotary tool device for a press machine using a device 100 for converting linear motion into rotary motion according to the present invention.

FIG. 8 is a drawing of an embodiment in which a reamer is attached to a tool chuck in a rotary tool device for a press machine using a device 100 for converting linear motion into rotary motion according to the present invention.

FIG. 9 is a diagram of a second embodiment of a rotary tool device for a press machine using the device 100 for converting linear motion into rotary motion according to the present invention.

FIG. 10 is a view of a third embodiment of the rotary tool device for a press machine according to the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Rotating tool device for press machines 3 Upper member 5 Lower member 11 Main body 15 Gas spring unit 21 Pressing head member 29 Male screw shaft member 33 Female screw member 41 Impact absorbing member 47 Lead nut 51 Lead screw member 89 Die 91 Impact absorbing member holder 93 Material support member 95 Impact absorbing member 97 Shoulder screw 100 Device for converting linear motion to rotary motion 200 Device for converting linear motion to rotary motion D Die DH Die mounting hole DR Drill PH Punch mounting hole R Reamer S Impactor SP Lifter spring T rotary tool W material

Claims (13)

[Claims] 1. A device provided with a linear motion by a pressing means, a main body 11 including a cylindrical upper member 3 and a lower member 5, and an upper member 3 of the main body 11 which is reciprocally movable in an axial direction. Is mounted inside the upper member of the main body 11 and the pressing head member 21 that is pressed and driven in the axial direction by the pressing means, and urges the pressing head member 21 in the direction opposite to the pressing direction by the pressing means. Urging means, which is connected to the pressing head member 21, and is given an axial movement through the pressing head member 21.
1, the male screw shaft member 29 which rotates by the axial movement by screwing with the female screw member 33 provided on the upper member 3, the lower surface of the female screw member 33 provided inside the upper member of the main body 11, and the main body. 11 and a shock absorbing member 41 provided between the lower member and the upper surface of the lower member, and a spline engagement provided at the shaft end of the male screw shaft member 29 for transmitting the rotation of the male screw shaft member 29 to the driven shaft side. A device for converting linear motion into rotary motion, characterized by comprising a shaft portion 43. 2. An apparatus for converting linear motion, which is axially reciprocally supported in a punch mounting hole of a press machine, into rotary motion, a main body 11 comprising a cylindrical upper member 3 and a lower member 5. A pressing head member 21 provided on the upper member 3 of the main body 11 so as to be capable of reciprocating in the axial direction and being pressed and driven in the axial direction by the pressing means of the press machine;
Biasing means mounted inside the upper member of the main body 11 for generating a repulsive force in a direction opposite to the pressing direction of the pressing head member 21 of the press machine is connected to the pressing head member 21. And a lower member 5 of the main body 11 which is axially moved by the axial movement of the main body 11 and is screwed with a female screw member 33 provided on the upper member 3 of the main body 11 so as to rotate with the axial movement. The lead nut 47 attached to the lead nut support 9 provided in the attachment hole of the lead nut and the lead nut 47 rotatably provided to the main body 11 by the bush 59 provided in the lead nut support 9 and the lead nut. A lead screw member 51 that is screwed into the lead screw 47 and a chuck protection ring member 73 that is provided at the lower end of the lead nut support 9 can be reciprocated by a certain amount in the axial direction. A blank holder 75 which is provided with elastically interposed,
Provided in the upper member of the main body 11 is an axial speed difference absorbing shaft connecting means formed by spline-engaging the spline engaging shaft portion 43 of the male screw shaft member 29 and the spline engaging hole of the lead screw member 51. An apparatus for converting linear motion into rotary motion, comprising a shock absorbing member 41 provided between the lower surface of the internal thread member 33 and the upper surface inside the lower member of the main body 11. 3. The device for converting linear motion into rotary motion according to claim 1, wherein the biasing means is a gas spring unit 15. 4. The shock absorbing member 41 is a disc spring or a urethane rubber spring.
An apparatus for converting linear motion according to claim 2 into rotary motion. 5. The shock absorbing member 41 is a disc spring or a urethane rubber spring.
A device for converting the linear motion described in 1. into a rotary motion. 6. An apparatus which is given a linear motion by a pressing means, a main body 11 including a cylindrical upper member 3 and a lower member 5, and an axially reciprocable upper member 3 of the main body 11. And a pressing head member 21 that is pressed and driven in the axial direction by a pressing means of a press machine, and is mounted inside an upper member of the main body 11,
1 is connected to the urging means for generating a repulsive force in the direction opposite to the pressing direction by the pressing means of the press machine, and is connected to the pressing head member 21 and is given an axial movement therefrom.
Female screw member 33 provided on the upper member 3 of the main body 11
The main body 1 is screwed with a male screw shaft member 29 that rotates along with the axial movement and a lead nut 47 that is fixedly attached to the lower member 5 of the main body 11 in a replaceable manner.
1, a lead screw member 51 for rotatably supporting the rotary tool T, and an axial speed difference absorbing shaft for spline-engaging the male screw shaft member 29 and the lead screw member 51 so as to be relatively displaceable in the axial direction. Connecting means and the main body 1
1 includes a shock absorbing member 41 provided between the lower surface of the female screw member 33 provided in the upper member and the upper surface of the lower member of the main body 11. apparatus. 7. A rotary tool device for a press machine, which is supported in a punch mounting hole of a press machine so as to be capable of reciprocating in an axial direction. A main body 1 comprising a cylindrical upper member 3 and a lower member 5.
1, a pressing head member 21 provided on the upper member 3 of the main body 11 so as to reciprocate in the axial direction and driven to be pressed in the axial direction by the pressing means of the press machine, and inside the upper member of the main body 11. Mounted on the pressing head member 2
1 is connected to the urging means for generating a repulsive force in the direction opposite to the pressing direction by the pressing means of the press machine, and is connected to the pressing head member 21 and is given an axial movement therefrom.
Female screw member 33 provided on the upper member 3 of the main body 11
And a lead nut 47 mounted on a lead nut support body 9 provided in a mounting hole of the lower member 5 of the main body 11, and the lead nut. A lead screw member 51 which is rotatably and axially slidable with respect to the main body 11 by a bush 59 provided on the support body 9 and is screwed into the lead nut 47, and a hollow shaft of the lead screw member 51. A support shaft 67 of a tool chuck 65 is elastically mounted on the portion 61 in the axial direction, and is mounted on a chuck protection ring member 73 provided on the lower end of the lead nut support 9 so as to be capable of reciprocating a certain amount in the axial direction. The plate retainer 75, the spline engaging shaft portion 43 of the male screw shaft member 29, and the spline engaging hole of the lead screw member 51 are provided by spline fitting. Rotary tool device for a press machine, characterized in that the shock absorbing member 41 is provided between the lower surface of the upper member female screw member 33 provided on the upper surface of the lower member of the body 11 of the 11. 8. The rotary tool device for a press machine according to claim 6, wherein the urging means is a gas spring unit 15. 9. The shock absorbing member 41 is a disc spring or a urethane rubber spring.
Alternatively, the rotary tool device for a press machine according to claim 7. 10. The rotary tool device for a press machine according to claim 6, claim 7, claim 8 or claim 9, wherein the rotary tool T is a tap, a reamer, or a drill. 11. A device for converting linear motion into rotary motion by a pressing means of a press machine, a main body 11 comprising a cylindrical upper member 3 and a lower member 5, and an axial direction of the upper member 3 of the main body 11. And a pressing head member 21 that is reciprocally provided in the upper part of the main body 11 and is pressed and driven in the axial direction by the pressing means of the press machine. An urging means for generating a repulsive force in a direction opposite to the pressing direction by means of an internal thread member 33 provided on the upper member 3 of the main body 11 and connected to the pressing head member 21 for axial movement. Screwing the male screw shaft member 29 that rotates with the axial movement and the lead nut 47 that is fixedly attached to the lower member 5 of the main body 11 in a replaceable manner. Lead screw member 51 rotatably supported to hold the rotary tool T, and the male screw shaft member 29.
And an axial speed difference absorbing shaft connecting means for spline-engaging the lead screw member 51 and the lead screw member 51 so as to be relatively displaceable in the axial direction. An apparatus 200 for converting linear motion into rotational motion is reciprocated in the punch mounting hole PH in the axial direction. A die 89 having a shock absorbing member 95 mounted movably therein and having a shock absorbing member 95 mounted between the shock absorbing member holder 91 and the material supporting member 93 is attached to the die mounting hole D.
A rotary tool device for a press machine, which is mounted on H. 12. The rotary tool device for a press machine according to claim 11, wherein the shock absorbing member 95 is urethane rubber or a disc spring. 13. The rotary tool device for a press machine according to claim 11 or 12, wherein the rotary tool T is a tap, a reamer, or a drill.