JP2981138B2 - Device for converting linear motion into rotary motion and rotary tool device for press machine using the device - Google Patents

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 or drilling or 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 apparatus for a press machine related to the present invention, there is Japanese Utility Model Laid-Open No. 04-51323. This conventional technique 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 be able to reciprocate in an axial direction, and is pressed and driven in an 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 axial movement, and that rotates with the axial movement by screwing with a female screw member provided on the device body; and a screw shaft member provided on the device body. A lead screw member which is screwed with a lead nut and is rotatably supported by the apparatus main body and holds a tapping tool; and the screw shaft member and the lead screw member are spline-engaged so as to be relatively displaceable in the axial direction. Tapping device for a press machine comprising an axial speed difference absorbing means ".

[0003]

The conventional tapping apparatus for a press described above has several problems for the following reasons. In a tapping device for a press, the linear motion is changed to a rotational motion when the tapping device is lowered by hitting the punch head with a press or a hitting element of the punch press, and the plate retainer at the bottom of the tapping device body contacts the material. By this means, the linear motion of the screw shaft member is converted into a rotary motion.

By the way, hit rate (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 second. Assuming that the stroke of the striker is 32 mm, the striker moves at a speed of about 0.1 second. Therefore, when the above-described conventional tapping device for a press machine is used in such a punch press, the plate retainer attached to the lower portion of the main body collides with the material at a very high speed, and at the moment of the collision, the linear motion moves. A large impact load is applied to the means for changing the rotational motion into a rotational motion, that is, a portion composed of 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. Immediately thereafter, the screw shaft member starts rotating by means for changing this linear motion into a rotary motion, and the original screw shaft member starts rotating. The tapping process is started. In the conventional tapping device for presses, there is a problem that a large impact load changes the linear motion into the rotary motion, that is, the screw shaft member and the female screw member are adversely affected, and the life thereof is shortened. Further, there is also a problem that the impact of the impact load causes dents in the material by the plate retainer, thereby lowering the product value.

By the way, in a normal punch press, a gap between a punch (male type) and a die (female type), that is, a so-called feed clearance (a material feeding gap of a workpiece) is about 20 mm. Therefore, there is no problem in the feeding of a flat sheet metal material, but when tapping is performed on a sheet metal material that has been formed by bending or the like with a tapping mold,
The size of this feed clearance is important. That is, if the feed clearance becomes small, there is a problem in that the material formed by molding with a large rise interferes with the punch (male type) and the die (female type) so that the material cannot be fed.

When tapping is performed by a tapping die, it is necessary to rotate the tap at least seven times. In other words, two rotations in the biting process of the tap material,
This is because about 5 rotations are required for the screw processing step. If means for changing the above-mentioned linear motion into rotary motion in order to give the tap seven rotations, that is, if the lead of the screw of the screw shaft member and the female screw member is set to 4 mm, only the conversion process into this rotary motion will be performed, 28 mm of the stroke amount of the striker of the press will be used. If the screw lead is 3mm, this will be 21mm and the difference is 7mm
Becomes Since this 7 mm can be used for the feed clearance, it is more advantageous to use a screw with a lead of 3 mm.

However, if the screw lead 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 a conventional punch press or tapping apparatus for a press, it has been difficult to reduce the lead of the screw and increase the feed clearance.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and an object of the present invention is to provide a device for converting a linear motion into a rotary motion by an impact load, in which the impact load generated in the conversion device is reduced. It is an object of the present invention to provide a device for converting a linear motion with good durability into a rotary motion.

It is another object of the present invention to provide a rotary tool device for a press machine which prevents a dent due to a plate presser from being formed on a processed product and has a sufficient feed clearance.

[0011]

According to a first aspect of the present invention, there is provided an apparatus for converting a linear motion into a rotary motion, wherein the linear motion is provided by a pressing means. A main body made of a member, a pressing head member which is provided on an upper member of the main body so as to be able to reciprocate in the axial direction, is driven to be pressed in the axial direction by the pressing means, and is mounted inside the upper member of the main body; An urging means for urging the pressing head member in a direction opposite to a pressing direction by the pressing means, and an axial movement connected to the pressing head member and given an axial movement through the pressing head member, and A male screw shaft member that rotates by the axial movement by screwing with a female screw member provided on the member,
An impact 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 in a lower member of the main body, and for transmitting rotation of the male screw shaft member to a driven shaft side. And a spline engagement shaft provided at the shaft end of the male screw shaft member.

According to a second aspect of the present invention, there is provided an apparatus for converting a linear motion into a rotary motion, the linear motion being reciprocally supported in an axial direction in a punch mounting hole of a press machine. A main body comprising an upper member and a lower member, a pressing head member provided on the upper member of the main body so as to be able to reciprocate in the axial direction, and being pressed and driven in the axial direction by a pressing means of the press machine; Biasing means mounted inside the upper member of the main body for generating a repulsive force in a direction opposite to a pressing direction of the pressing head member by the pressing means of the press machine; and an axial line connected to the pressing head member and connected thereto. A male screw shaft member which is given a directional movement and which rotates with an axial movement by screwing with a female screw member provided on the upper member of the main body; and a mounting hole of a lower 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 provided on a chuck protection ring member provided at a lower end of the lead nut support so as to reciprocate by a predetermined amount in the axial direction, a spline engagement shaft portion of the male screw shaft member, and the lead screw; An axial speed difference absorbing shaft connecting means formed by spline engagement with a spline engagement hole of the member, and between 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.

According to a third aspect of the present invention, there is provided a device for converting a linear motion into a rotary motion, wherein the biasing means is a gas spring unit in the first or second aspect.

Further, according to a fourth aspect of the present invention, in the apparatus for converting a linear motion into a rotary motion, the impact absorbing member is a disc spring or a urethane rubber spring in the first or second aspect.

According to a fifth aspect of the present invention, there is provided an apparatus for converting a linear motion into a rotary motion according to the third aspect, wherein 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, wherein a linear motion is given by a pressing means, wherein a main body comprising a cylindrical upper member and a lower member, and A pressing head member that is provided so as to be able to reciprocate 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,
Urging 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 axial movement therefrom, and that rotates 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 rotatably supported by the main body and screwably engaged with a lead nut fixedly attached to the member so as to be exchangeably fixed to the member, and a lead screw member holding a rotating tool, and the male screw shaft member and the lead screw member being axially opposed to each other; An axial speed difference absorbing shaft connecting means which is displaceably spline-engaged; and an impact 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 in a lower member of the main body. It is provided with.

A rotary tool device for a press machine according to a seventh aspect of the present invention is a rotary tool device for a press machine supported in a punch mounting hole of the press machine so as to be able to reciprocate in the axial direction. A main body, a pressing head member provided on the upper member of the main body so as to be able to reciprocate in the axial direction, and being pressed and driven in the axial direction by the pressing means of the press machine; and a main body mounted inside the upper member of the main body. ,
Urging 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 axial movement therefrom, and that rotates 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 provided in a mounting hole of the member; and a bush provided on the lead nut support, the lead being provided so as to be rotatable and axially slidable with respect to the main body. A lead screw member screwed to the nut and a support shaft of a tool chuck provided in the hollow shaft portion of the lead screw member by being elastically mounted in the axial direction, and a chuck protection ring member provided at a lower end of the lead nut support. A plate retainer provided so as to be reciprocally movable by a predetermined amount in the axial direction, a spline engagement shaft portion of the male screw shaft member, and a spline engagement hole of the lead screw member. 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, in the rotary tool device for a press machine according to the ninth aspect, the impact absorbing member is a disc spring or a urethane rubber spring in the sixth or seventh aspect.

According to a tenth aspect of the present invention, there is provided a rotary tool device for a press machine according to the sixth, seventh, eighth or ninth aspect, wherein the rotary tool is a tap, a reamer or a drill. .

[0021]

According to the first or second aspect of the present invention, the apparatus for converting a linear motion into a rotary motion can be used when a pressing head member is hit with a pressing means, for example, a punch press or a hitting element of a press. 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 the linear motion into the rotary motion is reduced.

According to a third aspect of the present invention, a device for converting a linear motion into a rotary motion is provided. In addition to the function of the first or second aspect, an appropriate mounting load is applied to the urging means. Moreover, the spring constant can be reduced.

According to the fourth aspect of the present invention, in addition to the function of the first or second aspect, an appropriate load can be applied to the shock absorbing member with a short stroke in addition to the function of the first or second aspect. It is possible to give.

Further, by providing a device for converting a linear motion into a rotary motion according to the fifth aspect, in addition to the function of the third aspect, it is possible to apply an appropriate load to the shock absorbing member with a short stroke. Become.

According to the rotary tool device for a press machine according to the sixth or seventh aspect, when the pressing head member is hit by a pressing means, for example, by a punch press or a hitting element of the press, an impact is applied. Since the absorbing member absorbs the impact load, the impact load applied to the male screw member and the female screw member of the device that converts the linear motion into the rotary motion is reduced.

According to a rotary tool device for a press machine as set forth in claim 8, the above-mentioned claim 6 or claim 7 is provided.
In addition to the above-described operation, an appropriate mounting load can be applied to the urging means, and the spring constant can be reduced.

Further, by providing the rotary tool device for a press machine according to the ninth aspect, in addition to the function of the sixth or seventh aspect, it is possible to apply an appropriate load to the shock absorbing member with a short stroke. It becomes possible.

According to a tenth aspect, in the rotary tool device for a press machine using a tap, a reamer or a drill as the rotary tool device, the same operation as the sixth, seventh, eighth or ninth aspect is performed. can get.

[0029]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below 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 according to the present embodiment and a rotary tool device 1 for a press machine using the device. The state where it is mounted in the punch mounting 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 includes an upper member 3 and a lower member 5 fixedly connected to each other by a plurality of bolts 2, and a lead removably fitted and mounted in a mounting hole 7 of the lower member 5. It has a cylindrical main body 11 constituted by the 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 at a fixed position with respect to the upper turret disc UT by a lifter spring SP. 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 disk UT to regulate rotation in the punch mounting hole PH. Have been.

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 cylinder part 17 of the gas spring unit 15 is mounted on each of the three. This gas spring unit 1
The fifth piston rod 19 projects upward, and the upper end of the piston rod 19 is connected and fixed to the pressing head member 21 with a plurality of bolts 22. The gas spring unit 15 is a bias that generates a repulsive force that pushes back the pressing head member 21 in a direction opposite to the pressing direction by the hitting element S as the pressing means of the turret punch press, that is, in the upward direction in FIG. Means.

The gas spring unit 15 is one urging means for generating a repulsive force for pushing the pressing head member 21 upward, and is not necessarily limited to the gas spring unit.
It is also possible to apply a repulsive force for pushing back upward by a compression coil spring or another 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 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 even if the plate thickness of the processing material is somewhat increased, the rate of increase of the pressing force on the material is small, so that no dent is formed on the material. Coil springs are damaged by fatigue in a short time when used at high stress, but gas springs are not damaged by fatigue when used at high stress and are more durable than coil springs.
On the other hand, coil springs have the advantage of being cheaper than gas springs.

The pressing head member 21 is provided so as to be reciprocable in the axial direction with respect to the main body 11 by the piston rod 19, that is, in the direction in which the striker S reciprocates vertically in FIG. , And has a flat upper surface 23 facing the striker S. The upper end of a male screw shaft member 29 composed of a ball screw shaft or a roller screw shaft by a thrust bearing 25 and a radial bearing 27 is attached to the pressing head member 21.
9 are rotatably connected around the axis.

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

A key 35 is provided on the outer periphery of the female screw member 33.
The key 35 is engaged with a key groove 37 formed on the inner periphery of the upper member 3 so as to be slidable up and down. 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.
Are provided. 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.

Accordingly, the rotation of the female screw member 33 with respect to the upper member 3 is restricted by the engagement between the key 35 and the key groove 37, and the female screw member 33 is always pressed upward. However, if a downward force greater than the repulsive force of the shock absorbing member 41 is applied to the female screw member 33, only the bending allowance 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 in 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 controlled by a spline engagement with a spline hole provided in a lead screw member 51 as a driven shaft described later. Conveyed by It is also possible to transmit the rotational motion of the male screw shaft member 29 by making the driven shaft side as a spline shaft and the rotation driving side as a spline hole and making spline engagement.

The lead nut support 9 has a set screw 45
Thus, the lead nut 47 is fixed and held. The lead nut 47 has a screw hole 49 on the same axis as the male screw shaft member 29, and the male screw portion 53 of the lead screw member 51 is screwed into the screw hole 49. The screw holes 49 and the screw leads of the male lead screw portion 53 are set to the same values as the screw leads of the taps 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. The spline member 55 is
A spline hole 57 is provided, and the spline hole 57 is spline-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-mentioned spline engagement which is relatively movable in the axial direction, there is a speed difference in the axial (vertical direction in FIG. 1) moving speed between the male screw shaft member 29 and the lead screw member 51. 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, the shaft connecting means is capable of absorbing a difference in the axial speed between the two shafts and transmitting the rotational motion or the rotational force.

The lead screw member 51 is rotatably supported in a bush 59 fitted in the lead nut support 9 and slidably in the axial direction.
The 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. A compression coil spring 69 is provided in the hollow shaft portion 61. The compression coil spring 69 acts between the stop pin 71 attached to the lead screw member 51 and the support shaft 67 to move the tool chuck 65 in the drawing. Biased downward. In the embodiment shown in FIG. 1, a tap as a tapping tool is mounted on the tool chuck 65.

A chuck protection ring member 73 and a plate holder 75 are attached to the lower end of the lead nut support 9 by bolts 77. Chuck protection ring member 73
Is fixed to the lower end of the lead nut support 9 by bolts 77, whereas the plate retainer 75 can be displaced in the axial direction by a predetermined amount with respect to the chuck protection ring member 73. This is urged downward in FIG. 1 by a 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 is moved in the axial direction in a direction approaching the chuck protection ring member 73. As shown in FIG. 9 of a second embodiment to be described later, a cutting fluid in a cutting fluid tank 81 is blown from a cutting fluid jet nozzle 85 to a tap through a cutting fluid passage (not shown). .

A lower turret disk LT is provided below the upper turret UT, and a die D is mounted in a die mounting hole DH of the lower turret disk 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 an initial state in which the striker S is in the ascending position. When the striker S descends from this state, the striker S comes into contact with the upper surface 23 of the pressing head member 21 and is moved in the axial direction. , That is, downward in the figure. Then, first, the entire body 11 descends with respect to the upper turret disk 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, as shown in FIG. 2, the plate holder 75 comes into contact with the upper surface of the material W on the die of the lower turret disk LT, and the main body 11 is further lowered. Then, the compression coil spring 79 bends and the chuck protection ring member 73
Abuts against the plate retainer 75. At this moment, the plate holder 7
The components 5, 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 are in a state where the downward movement is momentarily stopped.

At this time, a 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 a state where it has Therefore, the male screw shaft member 2
9 is subjected to an impact load. However, from that moment on, the female screw member 33 is pressed in the downward axial direction, and the shock absorbing member 41 bends, so that the male screw shaft member 29 also starts lowering and starts rotating at the same time. By bending the shock absorbing member 41 in this manner, the material W
The impact load at the time of abutment is greatly absorbed and relaxed (Fig. 2,
(See FIG. 3).

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

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

Further, the pumping action is performed by the axial movement until the plate holder 75 comes into contact with the chuck protection ring member 73, and the cutting fluid in the cutting fluid tank is jetted toward the tap.

When the pressing head member 21 is further pressed, the pressing head member 21 descends 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 continues to lower while rotating to a degree determined by the screw lead by screwing the male screw shaft member 29 and the female screw member 33. In this embodiment, the screw lead has a length of 3 mm. Therefore, the male screw shaft member 29
Moves 3 mm per rotation in the axial direction.

Assume that a punch press or a striker S of the press is used.
Assuming that the stroke is 32 mm, the tapping requires about 7 rotations in the actual tapping process, so that 21 mm (3 [3 [ mm / rotation] × 7 [rotation] = 21 mm), 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 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 moves in the axial direction while rotating to a degree determined by the screw lead. Is rotated while rotating, and a female screw is cut into the prepared hole of the material W.

In the tapping process, the male screw shaft member 29 is lowered in the axial direction with a degree determined by the lead of the male screw portion 31, while the lead screw member 51 is moved by the screw lead of the lead male screw portion 53. That is, it descends to a degree determined by the same screw lead as the tap for tapping. by the way,
Since the lead of the male screw part 31 is provided larger than the lead of the lead male screw part 53, the male screw shaft member 2
Numeral 9 rotates in the same direction at the same rotational speed as the lead screw member 51, but descends at a higher speed in the axial direction.

Accordingly, the axial movement amounts 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 so as to be mutually displaceable in the axial direction with spline engagement between the spline engagement shaft portion 43 and the spline hole 57 of the spline member 55, The male screw shaft member 29 and the lead screw member 51
Is rotated while sliding in the axial direction at the spline engaging portion, and the axial movement and rotation of the two are performed without hindering each other.

The tapping process is completed when the striker S is lowered to the lowermost 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 by the repulsive force of the gas spring unit 15. As a result, the male screw shaft member 29 is rotated in the reverse direction, the spline member 55 and the lead screw member 51 are all rotated in the reverse direction, and the male screw shaft member 29 and the lead screw member 51 rise with 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 moves further upward and returns to the initial state of FIG.

FIGS. 7 and 8 show a drill DR on a tool chuck 65 in a first embodiment of a rotary tool device for a press machine using a device 100 for converting a linear motion into a rotary motion according to the present embodiment. Alternatively, an example in which the reamer R is mounted is shown. FIG. 9 shows a second embodiment of a rotary tool device for a press machine using the device 100 for converting a linear motion into a rotary motion according to the present embodiment. 7, 8, and 9, the same components as those in the first embodiment are denoted by the same reference numerals.

The main configuration of the second embodiment shown in FIG. 9 is the same as that of the above-described first embodiment, and the operation and effect thereof are the same. Only the configuration and operation of the improved part will be described. In the second embodiment, the tool chuck 6 is used.
5, a rotary tool device for a press machine with a tap attached is shown.

Referring to FIG. 9, a cutting fluid tank 81 is mounted on a side surface of the upper member 3 and contains a cutting fluid. A cutting fluid nozzle 85 having a cutting fluid ejection port is provided in the vicinity of the tap, and the plate holder 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 is jetted from the cutting fluid nozzle 85 to the tap through a cutting fluid passage (not shown).

A ring-shaped elastic member 83 is provided between the chuck protecting member 73 and the plate holder 75 so as to be able to expand and contract. As the material of the elastic member 83, urethane rubber is used in the embodiment. 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 holder 75, the impact when the plate holder 75 collides with the material W is further reduced.

FIG. 10 shows the third rotary tool device for a press machine.
FIG. Referring 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, and the rotary tool device for a press machine 200 and a die 89.
Is the punch mounting hole PH of the upper turret disk UT
And coaxially mounted in a die mounting hole DH of the lower turret disk LT. In the embodiment shown in FIG. 10, a tap as a tapping tool is mounted on the tool chuck 65.

The structure of the device 200 for converting the linear motion into the rotary motion is exactly the same as that of the rotary tool device 1 for a press machine shown in FIG. 1, so that the description of the configuration is omitted.

As described above, the device 200 for converting a linear motion into a rotary motion has a shock absorbing member, and the die 89 has a shock absorbing function.

The die 89 includes a shock absorbing member holder 91, a material supporting member 93, a shock absorbing member 95, and the like. On the upper part of the shock absorbing member holding body 91, a plurality of shoulder screws 97 are provided with a material supporting member 93 which functions to flip up the processed material W to a position where the material W passes.
Thus, it 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 is regulated by the length of the shaft portion 96 of the shoulder screw 97. At the center of the material support member 93, a tool passage hole 99 through which the rotary tool T can pass is provided.

The shock absorbing member holding body 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. An absorbing member 95 is mounted. It is preferable that an elastic body such as urethane rubber or a disc spring is used for the shock absorbing member 95. The shock absorbing member mounting load is equal to or greater than the total of the mounting load of the urging means and the rotational resistance of the male screw shaft member 29 in the device 200 for converting the linear motion to the rotary motion. It is appropriate to set.

The operation of the rotary tool device for a press machine according to the third embodiment will now be described. When the striker S comes into contact with 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 a press machine is obtained. Body 11 against
Are lowered with respect to the upper turret disk UT.

Further, when the pressing head member 21 is pressed by the striker S to lower the main body 11, the plate holder 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 holder 75 is in contact with the upper surface of the material W, the compression coil spring 79 bends and the chuck protection ring member 73 contacts the plate holder 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 via the gas spring unit 17, the main body 11, and the plate holder 75. The shock absorbing member 95 mounted between them is compressed until the material supporting member 93 comes into contact with the shock absorbing member holding body 91.

The shock absorbing member holder 91 and the material supporting member 9
3, the striker S is still in contact with the pressing head member 21.
, The pressing head member 21 further descends against the upward repulsive force of the gas spring unit 17. As the pressing head member 21 descends, a linear motion is given to the male screw shaft member 29 in a downward direction, and the male screw shaft member 29 and the female screw member 33 are screwed 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 connected to the lead nut 4.
7, the lead screw member 51 moves in the axial direction while rotating to a degree determined by the screw lead.
Is rotated while rotating and a female screw is cut into the prepared hole of the material W.

The tapping process is completed when the striker S descends to the lowermost position. As the striker S rises, the pressing head member 21 moves as the striker S rises due to the repulsive force of the gas spring unit 15. Body 11
To move upward. Accordingly, the male screw shaft member 29 is reversely rotated, and accordingly, the spline member 55 and the lead screw member 51 are all reversely rotated, and each of the male screw shaft member 29 and the lead screw member 51 has a respective screw lead. 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 press machine of the third embodiment, the plate holder 75 is
The impact load generated when the upper surface of the material W is brought into contact with the upper surface of the material W is deflected by the impact absorbing member 95 provided on the die 89 and by the impact absorbing member 41 being flexed.
Absorption is alleviated as in the second embodiment.

In the rotary tool device for a press machine according to the third embodiment, an impact absorbing member is also provided on the die 89 side. In this way, it may be provided on both the die 89 side and the device for converting the linear motion into the rotary motion.

[0077]

As can be understood from the above description, according to the first or second aspect of the present invention, 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 reduced, and the life of the device that converts linear motion into rotary motion can be extended.

According to the third aspect of the present invention, the first aspect
Alternatively, in addition to the effects obtained by the second aspect of the invention, the spring constant can be reduced without changing the mounting load of the urging means, and the life of the urging means can be extended.

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

According to the fifth aspect of the present invention, in addition to the effect obtained by the third aspect of the invention, an appropriate load can be applied to the shock absorbing member with a short stroke, so that a compact linear motion can be obtained. It is possible to make devices that convert to rotary motion.

According to the invention of claim 6 or claim 7,
When the pressing head member is hit by, for example, a punch press or a hitter of the press by the pressing means, 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 reduced. , It is possible to extend the life of the device that converts linear motion into rotary motion,
Also, no dents are produced on the material by pressing 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 having irregularities such as “cut-and-raised” and “louver” can be fed between the die and the plate holder without any obstacle.

According to the eighth aspect of the present invention, in addition to the effect obtained in the sixth or seventh aspect, the spring constant can be reduced without changing the mounting load of the urging means. Even if the plate thickness changes, the change in the load applied to the plate holder can be reduced. As a result, even if the thickness of the material is increased, dents due to the pressing of the plate can be prevented.

According to the ninth aspect of the present invention, in addition to the effect obtained in the sixth or seventh aspect, an appropriate load can be applied to the shock absorbing member with a short stroke, so that a compact structure can be obtained. It is possible to make the device.

According to a tenth aspect of the present invention, there is provided a rotary tool device for a press machine using a tap, a reamer, or a drill as the rotary tool device according to any one of the sixth, seventh, eighth, and ninth aspects. The same effect can be obtained.

[Brief description of the drawings]

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

FIG. 3 is an operation explanatory view of one 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. 4 is an operation explanatory view of an embodiment of a device for converting linear motion into rotary motion and a rotary tool device for a press machine using the device according to the present invention.

FIG. 5 is a graph showing the relationship between the rotational resistance of a male screw member and time in a conventional apparatus for converting linear motion into rotary motion and a rotary tool apparatus for a press machine using the apparatus. The figure shown in comparison with that of the case.

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

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

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

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

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

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Rotary tool device for press machines 3 Upper member 5 Lower member 11 Main body 15 Gas spring unit 21 Press head member 29 Male screw shaft member 33 Female screw member 41 Shock absorbing member 47 Lead nut 51 Lead screw member 89 Die 91 Shock absorbing member holder 93 Material support member 95 Shock 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 Striker SP Lifter spring T Rotary tool W Material

Claims (10)

(57) [Claims] An apparatus provided with a linear motion by a pressing means, comprising: a main body comprising a cylindrical upper member and a lower member; A pressing head member 21 which is pressed and driven in the axial direction by the pressing means, and which is mounted inside an upper member of the main body 11 and urges the pressing head member 21 in a direction opposite to a pressing direction by the pressing means. The main body 1 is connected to the pressing head member 21 and is given axial movement through the pressing head member 21.
1, a male screw shaft member 29 that is rotated by the axial movement by screwing with a female screw member 33 provided on the upper member 3, and a lower surface of the female screw member 33 provided in the upper member of the main body 11 and the main body. 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 a linear motion into a rotary motion, comprising a shaft portion 43. 2. An apparatus for converting a linear motion supported by a punch mounting hole of a press machine in a reciprocating manner in an axial direction into a rotary motion, comprising: 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 able to reciprocate in the axial direction, and pressed and driven in the axial direction by a pressing means of the press machine;
An urging means which is mounted inside the upper member of the main body 11 and generates a repulsive force in a direction opposite to a pressing direction by the pressing means of the press machine, and which is connected to the pressing head member 21, A male screw shaft member 29 which is given axial movement by this and rotates with the axial movement by screwing with a female screw member 33 provided on the upper member 3 of the main body 11, and a lower member 5 of the main body 11 The lead nut 47 is provided rotatably with respect to the main body 11 by a lead nut 47 mounted on a lead nut support 9 provided in a mounting hole of the lead nut, and a bush 59 provided on the lead nut support 9, and the lead nut is provided. A fixed amount of reciprocating movement in the axial direction is possible with the lead screw member 51 screwed to the screw 47 and the chuck protection ring member 73 provided at the lower end of the lead nut support 9. A blank holder 75 which is provided with elastically interposed,
An axial speed difference absorbing shaft connecting means in which a spline engaging shaft portion 43 of the male screw shaft member 29 and a spline engaging hole of the lead screw member 51 are spline-engaged; provided in an upper member of the main body 11; An apparatus for converting a linear motion into a rotary motion, comprising: a shock absorbing member 41 provided between a lower surface of a female screw member 33 provided and an upper surface of a lower member of the main body 11. 3. The apparatus according to claim 1, wherein said urging means is a gas spring unit. 4. The apparatus according to claim 1, wherein said shock absorbing member is a disc spring or a urethane rubber spring.
An apparatus for converting a linear motion into a rotary motion according to claim 2. 5. The shock absorbing member 41 is a disc spring or a urethane rubber spring.
A device for converting a linear motion into a rotary motion according to the above. 6. An apparatus which is given a linear motion by a pressing means, wherein a main body 11 composed of a cylindrical upper member 3 and a lower member 5 is provided on the upper member 3 of the main body 11 so as to be able to reciprocate in the axial direction. A pressing head member 21 that is pressed and driven in the axial direction by a pressing means of a press machine;
1 is connected to the urging means for generating a repulsive force in a direction opposite to the pressing direction by the pressing means of the press machine, and is connected to the pressing head member 21 to give 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 in accordance with the axial movement and a lead nut 47 that is exchangeably fixed to the lower member 5 of the main body 11.
1, a lead screw member 51 rotatably supported and holding a 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. Connection means and the main body 1
1. A rotary tool for a press machine, comprising: a shock absorbing member 41 provided between a lower surface of a female screw member 33 provided in an upper member and an upper surface in a lower member of the main body 11. apparatus. 7. A rotary tool device for a press machine supported in a punch mounting hole of the press machine so as to be able to reciprocate in the axial direction, wherein a main body 1 comprising a cylindrical upper member 3 and a lower member 5 is provided.
1, a pressing head member 21 provided on the upper member 3 of the main body 11 so as to be able to reciprocate in the axial direction, and being pressed and driven in the axial direction by a pressing means of the press machine; And the pressing head member 2
1 is connected to the urging means for generating a repulsive force in a direction opposite to the pressing direction by the pressing means of the press machine, and is connected to the pressing head member 21 to give axial movement therefrom;
Female screw member 33 provided on the upper member 3 of the main body 11
A male screw shaft member 29 that rotates with an axial movement by screwing with the screw member, a lead nut 47 mounted on a lead nut support 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 rotatably and axially slidable with respect to the main body 11 by a bush 59 provided on the support 9 and screwed to the lead nut 47; and a hollow shaft of the lead screw member 51. The support shaft 67 of the tool chuck 65 is provided in the portion 61 by being elastically mounted in the axial direction, and is mounted on the chuck protection ring member 73 provided at the lower end of the lead nut support 9 so as to be able to reciprocate by a predetermined amount in the axial direction. The plate retainer 75 provided as described above, the spline engagement shaft portion 43 of the male screw shaft member 29 and the spline engagement 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 said urging means is a gas spring unit 15. 9. The apparatus according to claim 6, wherein the shock absorbing member is a disc spring or a urethane rubber spring.
Or a rotary tool device for a press machine according to claim 7. 10. The rotary tool device for a press machine according to claim 6, wherein the rotary tool T is a tap, a reamer, or a drill.