JP2821474B2 - Press forming machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a forward stroke (knockout amount) of a knockout pin when a blank (material) in a die is pushed out by the knockout pin.
The present invention relates to a knockout adjusting device in a pressure forming machine having a mechanism for adjusting the knockout.

[0002]

2. Description of the Related Art A forging machine for producing bolts, nuts, and other parts usually uses a blanking machine supplied from the side of a machine base at a forging station having opposing dies and punches. In this case, the forging process is performed step by step precisely. In this case, the forging machine is provided with a knockout pin for discharging a blank driven into the die from the inside of the die after molding.

[0003] The knockout pin is inserted into a pin insertion hole provided in the machine base, and the tip of the knockout pin is exposed in a die.
And the rear end is in contact with a knocker arm having a knocker, swinging the knocker arm by the movement of a connecting rod or the like in conjunction with the retreating movement of the punch, and by pushing with a knockout pin with the knocker of the knocker arm, These knockout pins are moved forward to project the blank from the inside of the die to the outside.

[0004] For example, forming of bolts and the like is performed by a multi-stage forging machine having a multi-stage forging station comprising a plurality of punches and a plurality of dies arranged opposite to each punch. In such a bolt, there is a case where a small diameter portion is required to be extended to the tip of a shaft portion where a screw is engraved, and in that case, a blank processing length differs in each process. And the knockout amount of each knockout pin accordingly (ie, the amount of protrusion)
Need to be adjusted.

Conventionally, as means for adjusting the knockout amount of such a knockout pin, for example, Japanese Unexamined Patent Publication No.
No. 52137 discloses a technique as shown in FIG.

In this technique, a knockout pin P is mounted on a machine base A so that its tip is inserted into a die (not shown), and swings around a spindle C outside the machine base A. The swing lever D is connected to the cams F and G provided on the cam shaft E.
Are provided so as to be vertically swung by rollers H and I which respectively engage with the swinging lever D. The swing lever D is swung via a cam shaft E in conjunction with the movement of a punch (not shown). On the other hand, a knocker arm K that rotates about a support shaft J is provided separately from the swing lever D, and a drive link M having a roller L is connected to one end of the knocker arm K so as to swing freely. A connecting member R rotatably supported by an adjusting screw Q provided on the fixing member N is connected to an intermediate portion of the driving link M, and the connecting member R is moved in the front-rear direction by rotating the adjusting screw Q. To change the distance a from the center of the support shaft C of the swing lever D to the rolling contact position of the roller L of the drive link M, thereby causing the knocker arm to swing. The swing amount of K is changed.

According to this, the swing amount of the knocker arm K that follows the swing of the swing lever D via the drive link M by the change of the distance a changes, and the knocker arm K moves the knockout pin P. The pushing amount changes, and therefore, the forward stroke (knockout amount) of the knockout pin P can be adjusted.

[0008]

In the technique shown in FIG. 6, the driving link M is moved from the support shaft C of the swing lever D.
By changing only the distance a to the rolling contact position of the roller L, the swing amount of the knocker arm K is changed. Therefore, when it is desired to adjust the knockout amount from a small knockout amount to a large knockout amount, the adjustment screw of the adjustment screw is required. The connecting member R must be largely moved in the front-rear direction together with the adjustment screw by performing a rotating operation for a long time. Therefore, it is necessary to set a large adjustment amount by the front-rear movement of the adjustment screw, and accordingly, the adjustment screw has to be adjusted accordingly. There was a problem that it took time to adjust by moving back and forth.

Accordingly, the present invention is capable of performing a wide stroke adjustment from a smaller forward movement stroke of the knockout pin to a larger forward movement stroke with a small amount of adjustment, and reducing the amount of adjustment of the adjusting member. It is another object of the present invention to provide a press forming machine including a knockout adjusting unit capable of shortening the time required for adjustment.

[0010]

That is, the present invention comprises a forging station in which a die 4 and a punch 6 are provided opposite to each other, and a knockout pin for projecting a blank out of the die behind the die 4. 22 is provided
A swing lever 35 that swings in conjunction with the forward and backward movement of the punch 6 by rotation of the cam shaft 17 ;
By swinging in conjunction disposed upward the swing of the該揺Do lever 35 a forging press equipped with a knocker arm 37 to push the knock-out pin 22,
The swing lever 35 and the knocker arm 37 are provided with a lever portion 35a and an arm portion 37a extending rearward, respectively, so as to face each other.
a, sliding surfaces 35b and 37b are formed on the opposite surfaces of the lever portion 35a and the arm portion 37a, respectively.
, Both ends are in sliding contact with both sliding contact surfaces 35b, 37b.
A drive link 41 is provided, and the drive link 41 and a fixing member 42 opposed to the drive link 41 are provided.
And a four-joint link mechanism A including a pair of first and second links 43 and 45 for connecting the drive link 41 and the fixed member 42. The first link 43 of the four-joint link mechanism A is provided. One end of the drive link 41 is located at a middle portion in the longitudinal direction of the drive link 41, and the other end of the second link 45 is located at the drive link side pivotal support of the first link 43 of the drive link 41 and one end of the drive link 41. , Respectively, and the second link 45
Is moved in the front-rear direction so that the drive link 4 around the drive link-side pivot point of the first link 43 becomes the center.
By varying the inclination angle of the longitudinal direction of 1,該駆
Both ends of the moving link 41 and the lever portion of the swing lever 35
Of the sliding contact surface 35b and the knocker arm 37 at 35a
Each sliding contact position of the arm portion 37a with the sliding contact surface 37b
From the swing center of the swing lever 35 and the knocker arm 37
Distance so that when one gets longer, the other gets shorter
Further, a moving mechanism B for changing the swing amount of the knocker arm 37 is provided.

According to the above configuration, when the knockout amount is adjusted, the other end of the second link 45 of the four-link mechanism A provided between the swing lever 35 and the knocker arm 37 by the moving mechanism B. Move the pivot point back and forth,
By changing the inclination angle of the drive link 41 about the drive link side pivot point of the first link 43 in the front-rear direction, the swing amount of the knocker arm 37 can be changed, and the knockout amount by the knockout pin 22 can be adjusted. It becomes possible.

In this case, since the drive link 41 is supported by the first link 43 at the intermediate portion in the longitudinal direction, when the drive link 41 swings, the arm 37 moves from the swing fulcrum of the knocker arm 37 to the arm 37. And the distance from the pivot point of the swing lever 35 to the sliding contact position with the other end of the driving link 41 is simultaneously changed. Become, and
The change increases the distance on one side, while decreasing the distance on the other side. As a result, only the second link 45 is relatively small back and forth movement by the moving mechanism B, that is, with a little adjustment amount of the second link 45, Bruno Kkaamu
37, the swing amount of the knockout pin 22
It is possible to perform a wide range of stroke adjustment from a smaller front movement stroke to a larger front movement stroke.

[0013]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a schematic plan view of a multi-stage press forming machine according to the present invention. A die block 3 is disposed at a predetermined position on a machine base 2 of the press forming machine 1. 3 are provided with a plurality of dies 4... 4 from coarse to fine at regular intervals. In addition, the above die block 3
In front of the ram 5 mounted on the machine 2 in front of
The same number of punches 6 ... 6 as the dies 4 ... 4
Are formed so as to face each other, and a plurality of forging stations are formed, and a rear end of the ram 5 is integrated with a flywheel 8 which is rotated by a drive motor 7 of the forging machine 1. The ram 5 moves back and forth toward the die block 3 by being connected to the die block 3 via a connecting member 10.

A quill 11 and a cutter (not shown) for cutting the wire a into a predetermined size are provided on one side of the die block 3. A material supply means 12 for intermittently supplying a wire a to the quill 11 by a predetermined length at the rear position.
Are arranged. Further, on the die block 3, a material transfer chuck (not shown) for transferring a wire, a so-called blank, cut to a certain size by the quill 11 and a cutter (not shown) between a plurality of forging stations. ) Is provided, and a blank driven by punches 6 ... 6 is pushed out from the dies 4 ... 4 behind the dies 4 ... 4 as shown in FIG. Knockout pin means 14 is provided.

The drive mechanism of the material supply device 12, the chuck transfer means 13 and the knockout pin means 14 includes a pair of parallel link type rotary mechanisms 15 for rotating the crankshaft 9 for reciprocating the ram 5. , 15 to a camshaft 17 provided with a plurality of cam plates 16, 16a, 16b for protruding and driving the knockout pin means 14, while rotating the camshaft 17 via a chain transmission mechanism 18. The rotation is transmitted to the chuck opening / closing shaft 19 of the chuck transfer means 13 and the drive shaft 20 of the material supply means 12. Thereby, in synchronization with the advance / retreat operation of the ram 5, the material supply device 12, the chuck transfer means 13
And the knockout pin means 14 is driven.

Next, a description will be given of the knockout pin means 14 and the front / rear position adjusting means 21 for moving the means 14 back and forth to change the front / rear position of the tip portion in the die 4.

The knockout pin means 14 includes a knockout pin 22, a push rod 23 for moving the pin 22 back and forth, and an intermediate pin interposed between the knockout pin 22 and the push rod 23. 24. The front / rear position adjusting means 21 includes a motor 25 fixedly provided at an upper rear end of the machine base 2 and a motor 25.
A gear 28, which is driven via a transmission mechanism comprising a gear 26 fixedly provided at the tip of the gear 26, a gear 27 meshed with the gear 26, and a gear 29 meshed with the gear 28, are fixedly provided at the shaft end. And a screw sleeve 30 screwed into the machine base 2 from the rear end of the machine base 2.

Then, the screw sleeve 30 is rotated in a predetermined direction by the motor 25 via the transmission mechanism, so that the depth of the processing hole formed by the tip of the knockout pin 22 and the die 4 becomes a desired blank shape. The front and rear positions of the knockout pin 22 are adjusted so as to be changed together.

When the front / rear position of the knockout pin 22 is adjusted as described above, the knockout amount adjusting means 31 for adjusting the forward movement stroke of the knockout pin 22 is configured as follows. ing.

That is, a support shaft 32 is provided behind the cam shaft 17 in parallel with the cam shaft 17.
A plurality of arm portions 3 on which rollers 33, 33a, 33b rollingly contacting with the respective cam plates 16, 16a, 16b are pivotally supported.
One swing lever 35 integrally provided with the same number of lever portions 35a... 35a as the number of knockout pins 22 is rotatably supported.

Also, above the support shaft 32, the shaft 32
A support shaft 36 is provided in parallel with the above, and a knocker arm 37 for hitting the pressing rod 23 is rotatably supported on the support shaft 36. A knocker 38 for hitting the pressing rod 23 is attached to an upper end of the knocker arm 37. Further, a lever portion 35a of the lever portion 37a and the swing lever 35 of the knocker arm 37 are both extend rearward, and is provided so that the arm portion 37a and a lever portion 35a is opposed, and these arm portions 37a On the surface facing the lever portion 35a, arc-shaped sliding contact surfaces 35b and 37b for receiving an end portion of a drive link described later are formed, respectively.

The lever 35a and the arm 3
7a, a drive link 41 is provided at both ends of rollers 39, 40 which are in sliding contact with the sliding surfaces 35b, 37b.
Together it is, composed with the driving link 41, a fixed frame 42 which faces to the driving link 41, a first pair of connecting these drive link 41 and the fixed frame 42, a second link 43 and 45 A four-bar link mechanism A is provided. First link 43 of the four-bar linkage A
Has one end pivotally connected to a longitudinal middle portion of the drive link 41 by a pin 44, and the other end has a fixed frame 42.
The second link 45 is pivotally connected at one end thereof to an intermediate portion between the pin 44 and the roller 39 of the drive link 41 by a pin 46. The other end of the second link 45 has a screw shaft 4
7 is pivotally mounted by a pin 46a, and the screw shaft 47 is screwed to a cylindrical nut 49 which is rotatably supported on the fixed frame 42 only.

In this case, as shown in FIG. 2, the cylinder nut 49 is rotatably supported by a holding member 50 attached to the fixed frame 42 by fixing means such as bolts (not shown). A gear 51 is fixed to an end of the cylindrical nut 49, and a gear 53 provided on an output shaft 52 a of a pulse motor 52 mounted on an upper portion of the fixed frame 42 is interlocked with the gear 51. Are linked.

In this manner, the other end pin 46a of the second link 45 is moved in the front-rear direction by the screw shaft 47, the cylinder nut 49, and the pulse motor 52, and the drive link side pin 44 of the first link is moved. The moving mechanism B is configured to change the swing amount of the knocker arm 37 by changing the inclination angle of the drive link 41 in the front-rear direction around the center.

A base end of a rod 54 is pivotally supported at the end of the lever 35 a of the swing lever 35, and the end of the rod 54 is connected to the other end of the arm 37 a of the knocker arm 37. A spring member 56 inserted into the attached ball bearing 55 and fitted on the rod 54 is interposed between the tip of the rod 54 and the ball bearing 55, and the force of the spring member 56 The arm portion 37a of the knocker arm 37 is constantly urged toward the lever portion 35a side of the swing lever 35, and the drive link 41
Are always in contact with the sliding surface 37 of the arm portion 37.
b and the sliding portion 35b of the lever portion 35a.

In addition, as shown in FIGS. 3 and 5, the sliding contact surface 37b of the knocker arm 37 and the sliding contact surface 35b of the swing lever 35 are arc surfaces having the same radius of curvature. Further, the slide contact surfaces 35b and 37b are formed so as to be located on a circle having the same radius around the pin 44 at the protrusion end position. Thereby, even if the drive link 41 is swung in the front-rear direction about the pin 44 to adjust the forward movement stroke amount of the knockout pin 22,
The protrusion end position is always located at the same position.

In the head forming machine equipped with such a knockout amount adjusting means 31, after the head is pressed by the ram 5 and the punch 6, the punch 6 is moved from the die 4 to the punch 6.
The cam shaft 17 is rotated in conjunction with the backward movement of the cam plate 16, and the cam plates 16, 16a and 16b rotate from the position shown in FIG. 2 to the position shown in FIG. 3, and the swing lever 35 swings upward. Accordingly, the knocker arm 37 also swings from the projecting start position shown in FIG. 2 to the projecting end position shown in FIG. 3 via the drive link 41 of the four-bar linkage A, so that the knocker 38 moves the pushing rod 23. Hit the middle pin 24,
The blank is projected from the inside of the die 4 through the knockout pin 22.

Further, as the punch 6 moves from the backward movement to the forward movement, the cam plates 16, 16a and 16b further rotate from the position shown in FIG. 3 to the position shown in FIG. 2, and the swing lever 35 swings downward. At the same time, the knocker arm 37 also swings counterclockwise by the force of the spring member 56, and the knocker 38 separates from the pushing rod 23 to the rear, so that the knockout pin 22 and the intermediate pin 2 are driven by blanking.
4. Prepare for the retraction of the push rod 23.

The knockout amount adjusting means 3
In 1, if the pulse motor 52 is rotated in the normal rotation direction or the reverse rotation direction, the cylinder nut 49 rotates, and the screw shaft 47 moves back and forth according to the rotation direction. Is transmitted to the link 41
Swings about the pin 44 so that the drive link 4
The inclination angle about the pin 44 is changed.

In this case, since the drive link 41 has its lengthwise intermediate portion supported by the pin 44, the screw shaft 47 is moved backward from the state shown in FIG. 5, for example, as shown in FIG. By selecting a state in which the drive link 41 is tilted so that the upper roller 39 is positioned rearward and the lower roller 40 is positioned forward with the pin 44 as the center, the sliding contact surface 37b from the axis of the support shaft 36 is selected. And roller 39
The distance Xa from the axis of the support shaft 32 to the rolling contact position between the sliding contact surface 35b and the roller 40 is changed to be shorter, while the distance Xa to the rolling contact position with the roller shaft 40 becomes longer. Will be. Thereby, the vertical movement amount of the drive link 41 with respect to the swing of the swing lever 35 is adjusted to be small, and the swing amount of the knocker arm 37 with respect to the vertical movement of the drive link 41 is also adjusted at the same time. . Therefore, by the synergistic effect of the two adjustments, the amount by which the knocker 38 pushes the knockout pin 22 (that is, the knockout amount La) is changed to be smaller, as is apparent from FIG. become.

On the other hand, when the screw shaft 47 is moved forward from the state shown in FIG. 3 as shown in FIG.
The upper roller 39 is tilted so that the upper roller 39 is positioned forward and the lower roller 40 is positioned rearward about the pin 44. Thereby, while the distance Xb from the axis of the support shaft 36 to the rolling contact position between the sliding contact surface 37b and the roller 39 is reduced,
The distance Yb from the axis of the support shaft 32 to the rolling contact position between the sliding contact surface 35b and the roller 40 is changed to be longer.

As a result, the vertical movement of the drive link 41 with respect to the swing of the swing lever 35 is adjusted to be large, and the swing of the knocker arm 37 with respect to the vertical movement of the drive link 41 is also simultaneously large. Will be adjusted. Therefore, the screw 4
7, the amount by which the knocker 38 pushes the knockout pin 22 (that is, the knockout amount Lb) is changed to a greater extent as shown in FIG.

As described above, the screw shaft 4 is
It is possible to perform a wide range of stroke adjustments from a smaller forward movement stroke of the knockout pin to a larger forward movement stroke with only a relatively small amount of movement of the knockout pin 7 relative to the fixed frame 42. .
As described above, the amount of adjustment of the second link 45, in other words, the screw shaft 47 can be reduced, so that the time required for adjustment can be reduced.

In the above embodiment, the multi-stage press forming machine 1 is taken as an example. However, it goes without saying that the present invention can be applied to a single-stage press forming machine. In other words, in the case of manufacturing bolts having different shaft lengths little by little, it is necessary to adjust the knockout amount of the knockout pin each time to match the processing length of the forged product. The present invention can effectively cope with such a case.

In the above embodiment, the cylinder nut 49 is rotated by the pulse motor 52 to move the second link 45 back and forth by the reciprocation of the screw shaft 47. For example, the screw shaft 47 and the cylinder Instead of the moving mechanism using the nut 49 and the pulse motor 52, the moving mechanism may be configured to be moved back and forth by, for example, a fluid pressure cylinder.

Further, the second link 45 is connected to the drive link 4
1 and the lower roller 40 of the drive link 41 and the pin 4
Needless to say, it may be arranged at an intermediate portion between the first and fourth members.

The spring force urging means for constantly urging the knocker arm 37 toward the swing lever 35 is provided between the knocker arm 37 and the swing lever 35 as described above. A spring force urging means may be provided between 37 and the machine base 2, and the knocker arm 37 may be constantly urged toward the swing lever 35 by the spring force urging means.

[0039]

As described above, according to the present invention, when adjusting the knockout amount, the second mechanism of the four-joint link mechanism A provided between the swing lever 35 and the knocker arm 37 by the moving mechanism B is used. By moving the pivot point at the other end of the link 45 in the front-rear direction and changing the inclination angle of the drive link 41 in the front-rear direction about the drive link-side pivot point of the first link 43, the swing of the knocker arm 37 is changed. The distance from the pivot point to the sliding contact position of the arm 37 with one end of the drive link 41 and the distance from the pivot point of the swing lever 35 to the sliding contact position of the lever 35 with the other end of the drive link 41 are set. at the same time,
In addition, while the distance on one side is longer, the distance on the other side can be changed to be shorter, so that the movement mechanism B can move the second link 45 relatively back and forth only by a relatively small amount. That is, it is possible to perform a wide range of stroke adjustment from a smaller forward movement stroke of the knockout pin 22 to a larger forward movement stroke with a small adjustment amount, and accordingly, the adjustment amount of the second link 45 can be reduced. Thus, the time required for the adjustment can be reduced.

[Brief description of the drawings]

FIG. 1 is a plan view of a multi-stage press forming machine according to the present invention.

FIG. 2 is an enlarged view of a part of a knockout amount adjusting means of the forging machine.

FIG. 3 is an enlarged view of a part of a knockout amount adjusting means showing the protruding state.

FIG. 4 is an enlarged view of a portion of a knockout amount adjusting means showing a state in which the knockout amount is changed to be large.

FIG. 5 is an enlarged view of a portion of a knockout amount adjusting means showing the protruding state.

FIG. 6 is an explanatory diagram of a conventional knockout amount adjusting mechanism.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 pressure forming machine 2 machine stand 3 die 6 punch 14 knockout pin means 16, 16a, 16b cam plate 17 camshaft 22 knockout pin 31 knockout amount adjusting means 35 rocking lever 35a lever portion 35b sliding contact surface 37 knocker arm 37a arm Part 37b Sliding contact surface 41 Drive link 42 Fixed frame 43 First link 44, 44a Pin 45 Second link 46, 46a Pin 47 Screw shaft 49 Cylinder nut 52 Pulse motor 24 Knockout pin A Four-node link mechanism B Moving means

Claims (1)

(57) [Claims] 1. A stamping station having a die 4 and a punch 6 opposed to each other, a knockout pin 22 for projecting a blank out of the die behind the die 4 , and a camshaft. The swing lever 35 swings in conjunction with the forward and backward movement of the punch 6 by the rotation of the punch 17.
And a knocker arm 37 disposed above the swing lever 35 and swinging in conjunction with the swing of the swing lever 35 to push the knockout pin 22. The swing lever 35 and the knocker arm 37 each have a lever portion 35a extending rearward.
And the arm portion 37a are provided in opposition to each other, and sliding surfaces 35b and 37b are formed on opposing surfaces of the lever portion 35a and the arm portion 37a, respectively. Has two sliding contact surfaces 35b,
A drive link 41 having both ends slidingly in contact with 37b is provided.
In addition, the drive link 41, a fixed member 42 facing the drive link 41, and a pair of first and second links 43, 4 connecting the drive link 41 and the fixed member 42.
5 is provided, one end of the first link 43 of the four-link mechanism A is located at a middle portion in the longitudinal direction of the drive link 41, and the second link 45 is one end of the drive link 41. Parts of the drive link 41 are pivotally supported at an intermediate portion between the drive link side pivotal support portion of the first link 43 and one end of the drive link 41, and the fixed member 42 has the second link 45 the other end pivot point is moved in the longitudinal direction, by changing the inclination angle of the longitudinal direction of the drive link 41 about the drive link side pivot point of the first link 43, and both ends of the driving link 41 The shaking above
The sliding contact surface 35b of the lever portion 35a of the moving lever 35
Sliding surface of the arm portion 37a of the knocker arm 37
The swing lever 35 and the knocker at each sliding contact position with 37b
When the distance from the swing center of the
A pressure forming machine characterized by comprising a moving mechanism B for changing the swing amount of the knocker arm 37 so that the other side is shortened .