JP2000280094A - Press machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a press machine using a toggle link which has a large variation ratio of slide stroke length, enables fine adjustment of a bottom dead point, and has small acceleration at a top dead point. SOLUTION: By rotation of an eccentric part 8A of a crank shaft 8, a slider 9 is moved upward/downward, and the end of an arm 6A extending over a fixing support point 5 of a toggle upper link 6 and the slider 9 are connected by a connection link 14 for connecting a driving link 11 and a drive connection link 12 at the connecting support point 13. A worm wheel 15 which is coaxial with the connecting support point 13 under the bottom dead point of the slide 3 is installed to a frame in a manner to adjust the rotation angle. Then, a second pin 17 at the tip end of a second arm 16 installed in a radial direction from the axis of the worm wheel 15, and the connecting support point 13 are connected with a third link 18, for restraining the movement of the connecting support point 13 on an arc. The position of the second pin 17 varies to adjust stroke length of the slide 3 and to maintain the bottom dead point constant.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a press machine in which a slide is moved up and down linearly using a toggle link, in which the stroke length of the slide is changed at a large change ratio and the bottom dead center is adjusted. It is effective for

[0002]

2. Description of the Related Art The rotation of an eccentric portion of a crankshaft is changed into a linear reciprocating motion via a connecting rod, and the reciprocating motion is input to a central connecting pin of upper and lower toggle links via a connecting link to linearly move a slide up and down. For example, as described in Japanese Patent Publication No. 7-55399, a press machine changes the rotation of an eccentric portion of a crankshaft into a linear reciprocating motion of a slider via a connecting piece, and connects the slider and a center connecting pin of a toggle link on both sides with a first link. The first link and the second link are connected by the connecting body to give a vertical movement to the slide, and the male screw connecting the third link and the fourth link forming a parallelogram with the first link and the second link is adjusted to the vertical position. Some adjust the stroke length of the slide and the bottom dead center.

Japanese Patent Laid-Open Publication No. Sho 48-42471 discloses a stroke length adjusting mechanism that can change a stroke length in two stages by fixing an eccentric shaft with a lock pin.

[0004]

[Problems to be Solved by the Invention] Japanese Patent Publication No. 7-55399
The press machine disclosed in (1) adjusts by changing the shape of the fourth link from the first link that forms a parallelogram by raising and lowering the male screw, so that even if the adjustment length of the male screw is increased, the stroke length of the slide The change ratio of the stroke is as small as about 4, and the amount of movement of the bottom dead center increases with the change of the stroke length of the slide. Even if fine adjustment of the bottom dead center is possible at a certain stroke length, the change of the stroke length There is a disadvantage that the ratio is small. Therefore, the height of the mold is limited. Further, a press machine using a toggle link generally has a disadvantage that acceleration at the time of reversal at the top dead center of the slide is large and high-speed operation is difficult.

The stroke length adjusting mechanism of a press machine disclosed in Japanese Patent Application Laid-Open No. 48-47271 cannot continuously change the stroke length. On the other hand, in the press machine disclosed in Japanese Patent Publication No. 7-55399, the stroke length can be continuously changed by using a screw mechanism as the stroke length adjusting mechanism. However, in this case, since a pressing load is applied to the screw mechanism during the pressing operation, the screw mechanism must have a robust structure, and the manufacturing cost has increased with the increase in the size of the machine.

SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned problems and to use a toggle link having a large change ratio of a stroke length of a slide, capable of fine adjustment of a bottom dead center, and having a small acceleration at a top dead center. An object of the present invention is to provide a press machine for raising and lowering a slide.

Still another object of the present invention is to reduce the size of the machine by enabling the stroke length to be continuously changed and reducing the press load applied to the screw mechanism used in the stroke length adjusting mechanism. It is to provide a press machine that can perform the press.

[0008]

According to the first aspect of the present invention, a slider (9) for rotating the crankshaft (8) up and down through a connecting rod (10), and one end of the slider (9). ) And drive link (11)
A drive connection link (12) connecting one end to the drive link (11); a member supported at one point by a fixed fulcrum so as to be swingable; one end connected to the drive connection link (12); Is a toggle upper link (6) connected to the slide (3) via a link member, and the drive link (1).
A press machine comprising: 1) a stroke length adjusting mechanism for restricting a swinging motion of a fulcrum connecting the drive connection link (12).

According to the invention, the change ratio of the stroke length can be increased as compared with the related art. Also,
It is possible to adjust the stroke length while keeping the die height, that is, the bottom dead center unchanged. Therefore, fine adjustment of the bottom dead center during the press operation, that is, so-called bottom dead center correction can be performed.

Further, according to the configuration of the present invention, since the top dead center side acceleration does not become extremely large, the vibration of the machine is reduced, so that it can be used for a press machine requiring high speed operation. . In addition, since a certain amount of space can be provided between the link member connected to the crankshaft and the slide, the degree of freedom of the pitch between points at the time of design increases.

Furthermore, by changing the position of the fulcrum connecting the drive link (11) and the drive connection link (12) at the top dead center position of the press machine, the press machine can be provided with a quick lift function. Here, the click lift function means that in a press machine with a short stroke length, during maintenance of dies and the like, slides are temporarily raised, the distance between dies is increased, and after maintenance is completed, the original die height is restored. Refers to the function to restore.

According to the second aspect of the present invention, the stroke length adjusting mechanism has a connecting fulcrum (13) erected on the drive link (11) and a third link connecting one end to the connecting fulcrum (13). (18), a shaft (15A) rotatably supported by the frame (31A), and one end of the shaft (15A).
A) a second arm fixed to A) and having the other end connected to the other end of the third link; and a rotating means for rotating the shaft. Item 4. A press machine according to item 1.

According to the invention, it is possible to obtain a press machine having a stroke length adjusting mechanism whose structure is simple and whose manufacturing cost is reduced as compared with the related art.

According to a third aspect of the present invention, the rotating means includes a worm wheel (15) fixedly mounted on the shaft (15A),
The press machine according to claim 2, further comprising a worm shaft (36) meshing with the worm wheel (15).

According to the invention, the stroke length can be continuously adjusted. In addition, it is possible to obtain a rotating unit that is smaller than other gear mechanisms.

According to a fourth aspect of the present invention, the stroke length adjusting mechanism has fixing means for fixing the shaft (15A), and the fixing means is a fixing cylinder which is movably fitted to the shaft (15A). (35) and a jaw (1) provided on the shaft (15A) for regulating the moving distance of the fixing cylinder (35).
5B), and a pressurized oil supply device for supplying pressurized oil between the jaw (15B) and the fixing cylinder (35). It is.

According to the invention, since the shaft (15A) connected to the rotating means can be fixed, the influence of the press load generated during the pressing operation on the rotating means can be reduced.

According to a fifth aspect of the present invention, the stroke length adjusting mechanism includes a pin (2) provided upright on the drive link (11).
3), a gear (24) provided with a guide groove (25) into which the pin (23) is movably fitted, and the gear (2).
The press machine according to claim 1, further comprising: gear rotation angle adjusting means for adjusting the rotation angle of (4).

According to the invention, the stroke length can be determined by the rotation angle of the gear (24), that is, the rotation angle of the guide groove (25). Therefore, it is possible to obtain a stroke length adjusting mechanism having a simple structure and a reduced manufacturing cost.

[0020]

1 to 12 show an embodiment of a press machine according to the present invention. The first shown in FIGS. 1 and 2
In the embodiment, a slide 3 guided up and down is provided on a frame (not shown) of the press machine 1, and an upper end of a toggle lower link 4 connected to the slide 3 and a lower end of a toggle upper link 6 connected to a fixed fulcrum 5 of the frame. To the center connecting pin 7
To form a toggle link. The eccentric part 8A of the crankshaft 8 and the slider 9 guided in the up and down direction by the frame are connected by a connecting rod 10 to give a vertical movement to the slider 9 to extend the toggle upper link 6 beyond the fixed fulcrum 5. 6A and the slider 9 and the drive link 11 and the drive connection link 12
3 are connected by a connection link 14 configured by connection.

At the two points 2 and 2 of the slide 3, the above-described configuration is provided, and the slide 3 is connected to the slider 9. The position of the bottom dead center of the slide 3, that is, as shown in FIG.
A worm wheel 15 concentric with the connection fulcrum 13 is rotatably provided on the frame with the eccentric portion 8A in the upward direction of the crankshaft 8, and a second arm 16 is provided extending from the shaft 15A of the worm wheel 15 in the radial direction. 2nd at the tip of
A pin 17 is provided, and the second pin 17 and the connection fulcrum 13
Linked by link 18. The details are shown in a three-dimensional view in FIG. Accordingly, when the eccentric portion 8A of the crankshaft 8 rotates and the slider 9 moves up and down, the connection fulcrum 13 is restrained from moving along an arc having the second pin 17 as a center and the third link 18 as a radius. The slide 3 is moved up and down by the drive link 11 and the drive connection link 12 via the toggle link.

The rotation angle of the worm wheel 15 is adjusted by a worm shaft 36 (FIG. 3) provided on the frame.
By changing the position of the second pin 17 around the axis 15A, the stroke length of the slide 3 can be changed. In this case, at the bottom dead center position of the slide 3, the center of the shaft 15A of the worm wheel 15 and the connection fulcrum 13 always coincide,
The bottom dead center position can be maintained at a fixed position without changing.

That is, the stroke length adjusting mechanism includes a drive link 11, a connection fulcrum 13, a third link 18, and a shaft 15.
A and the second arm 16 and a rotating means for rotating the shaft 15A. Further, the rotating means is constituted by the worm wheel 15 and the worm shaft 36.

If the center of the worm wheel 15 provided on the frame is eccentric with respect to the connection fulcrum 13 at the bottom dead center position of the slide 3, for example, is slightly eccentric in the vertical direction, the second pin 17 rotates around the shaft 15 A. By changing the position, the stroke length of the slide 3 is changed, and the position of the bottom dead center is also slightly changed. Therefore, the fine adjustment of the position of the bottom dead center of the slide 3 can be performed by finely adjusting the position of the second pin 17 using this.

The point of the slide 3 and the toggle lower link 4 are connected by a slide drive link 19, and one end of a dynamic equilibrium drive link 21 rotatably provided at a second fixed fulcrum 20 is connected to the lower end of the toggle lower link 4. When the dynamic balance weight 22 is configured to move up and down by the swing of the dynamic balance drive link 21 by connecting the other end to the dynamic balance weight 22, the inertial force due to the movement of the slide 3 portion Can be dynamically balanced.

In the first embodiment, the slide 3
Is the position of the top dead center, the second arm 16 is rotated from the range of the effective set angle to the upper limit of the rotatable angle, and the position of the second pin 17 is changed.
By changing the fulcrum of, a press-processed product to be produced is provided as a quick access to the mold for checking the condition inside the mold by inspecting a bolster (not shown) and a mold (not shown) attached to the slide 3. In addition to the die height setting set by the slide adjusting device in accordance with the above, the slide 3 is expanded upward, and has a quick lift function for accurately returning the die height to the original position.

In the first embodiment, the connecting fulcrum 1
Although the pins erected from 3 to the middle of the drive link 11 are at the same position as the connection fulcrum 13, the pins may be at any position between the connection fulcrum 13 and the middle of the drive link 11.

Here, in the first embodiment, the worm wheel 15 and the worm shaft 36 can be protected by preventing the rotation of the shaft 15A due to the press load.
The fixing means 40 for the shaft 15A is shown in FIG.

The third link connecting portion A-A shown in FIG.
FIG. 3A is a sectional view taken along line A. The fixing means 40 is provided with a fixing cylinder 35 operated by hydraulic pressure. The fixing cylinder 35 is fitted movably in the axial direction with the shaft 15A. On the other hand, a bush 37 for supporting the shaft 15A is provided on the frame 31A. Also, shaft 15A
Is provided with a jaw 15B. With the bush 37 and the jaw 15B, the moving distance of the fixing cylinder 35 is
It is regulated to be very small. The shaft 15A is provided with an oil passage 38 for supplying a hydraulic pressure for driving the fixing cylinder 35.

During press operation, the shaft 15A is fixed.
Pressure oil is supplied to the oil passage 38. Then, the fixing cylinder 35 moves in the direction of P. If you supply more pressure oil,
By the action of the pressure oil, the fixing cylinder 35 is
While being pressed against 7A, the shaft 15A receives a force in the direction of Q. Then, since the second arm 16 is fixed to the shaft 15A, the second arm 16 is pressed against the bush 37B. Thus, the shaft 15A is fixed.

Here, the second arm 16 receives a pulling force from the left and right shafts 15A via the second pins. At this time,
The second arm 16 is deformed, but its amount is very small.
There is almost no effect on the press operation.

In this way, the second load is
Even when the shaft 15A receives a force in the rotation direction via the arm 16, the worm wheel 15 does not rotate because the shaft 15A is fixed. Therefore, even during the press operation, the worm wheel 15 and the worm shaft 36 are protected.

In the second embodiment shown in FIG. 4, the slide 3 is raised and lowered by the rotation of the eccentric portion 8A of the crankshaft 8, and the dynamic balance weight 2
The configuration performed in 2 is the same as that of the first embodiment, and the description is omitted only with the reference numerals, and only different configurations will be described. FIG.
Shows a case in which the eccentric portion 8A of the crankshaft 8 is located below the crankshaft 8, and differs from the first embodiment in that the slide 3 is located at the top dead center. does not change.

In the second embodiment, a pin 23 is erected at a position on the way from the connecting fulcrum 13 at the distal end of the drive link 11 toward the slider 9 and the pin 23 is mounted on the frame (3).
1A) is guided and restrained by a guide groove 25 provided linearly on the side surface of the gear 24 provided in 1A). In this case, the center of the gear 24 coincides with the center of the pin 23 when the eccentric portion 8A of the crankshaft 8 is at the bottom dead center position of the slide 3 in which the eccentric portion 8A is located upward, and the gear 24 can freely rotate on the frame (31A). And fine adjustment of the rotation angle is possible, that is, gear rotation angle adjustment means is provided. The gear rotation angle adjusting means is constituted by, for example, a motor having a drive shaft having a pinion that meshes with the gear 24 and having an encoder for detecting the rotation angle. In the second embodiment, the guide groove 25 provided on the side surface of the gear 24 is linear.
The shape may be an arc.

The guide groove 2 is adjusted by adjusting the rotation angle of the gear 24.
By changing the inclination angle of 5, the stroke length of the slide 3 can be changed, and the position of the bottom dead center can be kept constant. Also, the center of the gear 24 is eccentric from the center of the pin 23, for example, is slightly eccentric in the vertical direction, so that the gear 24 is rotated to slightly change the inclination angle of the guide groove 25, and the bottom dead center of the slide 3 is changed. It is the same as the first embodiment that the position can be finely adjusted.

Further, in the second embodiment, the inclination angle of the guide groove 25 is changed by rotating the gear 24 from the range of the effective set angle to the upper limit angle at which the slide 3 can rotate at the position of the top dead center of the slide 3. As a result, as in the first embodiment, production is performed as quick access to the mold for checking the condition inside the mold by inspecting the mold (not shown) attached to the bolster and the slide 3 (not shown). While maintaining the die height setting set by the slide adjusting device 34 in accordance with the press-processed product, the slide 3 is enlarged upward, and has a quick lift function for accurately returning the die height to the original position.

FIG. 5 shows a mode in which the second embodiment is mounted on a frame 31A of a press machine 31. A pinion 26 meshing with the gear 24 is provided to adjust the rotational driving of the gear 24. Although the case where the gears 24 and 24 are provided so as to mesh with each other is shown, the design may be changed as appropriate according to the distance between the left and right points of the press machine 31. The same effect can be obtained even when the position of the pin 23 is provided until the position coincides with the connection fulcrum 13 or on the distant drive link 11. First
Similarly, the worm wheel 15 in the embodiment can be appropriately designed.

The lifting drive system for the slide 3 provided on the frame 31A is as described above. Slide 3
The plunger 27 erected at the point portion is guided by a guide 28 provided on the frame 2, and the post 29 erected downward is guided by a post guide 30 provided on a bed 32 of the frame 31 </ b> A so as to be able to move up and down freely. A slide adjusting device 34 is provided on the upper surface of the slide 3.

FIG. 6 shows that in the second embodiment, the angle of the gear 24 is adjusted, and the inclination angle of the guide groove 25 is set to 0 in the downward direction.
°, the stroke length of the slide 3 while the slider 9 moves up and down between the position corresponding to the top dead center of the slide 3 at the lower end and the position corresponding to the bottom dead center of the slide 3 at the upper end by the rotation of the crankshaft 8 FIG. 6 is a kinematic diagram of a driving mechanism showing that the change of the driving mechanism is performed. As the slider 9 moves up and down, the pins 23
Move while being constrained by the guide grooves 25 adjusted to the respective inclination angles, the center of the pin 23 always coincides with the center of the gear 24 at the bottom dead center of the slide 3, and therefore, the drive connection link 1
The connecting portion of the upper link 6 and the arm 6A of the toggle upper link 6 is at a fixed position, indicating that the bottom dead center of the slide 3 can be held at a fixed position.

FIG. 10A shows a stroke diagram of the slide 3 in the case of the second embodiment, and FIG. 10B shows the relationship of the stroke length of the slide 3 with respect to the inclination angle of the guide groove 25. As is clear from the stroke diagram of FIG. 10 (a), the stroke diagram of the press machine using the toggle link by this drive mechanism has a top dead center (crank angle 0 °).
A gentle curve is drawn in the vicinity, indicating that the acceleration due to the reversal of the slide 3 at the top dead center is small, and that it can cope with high-speed driving. In addition, the dwell time at the bottom dead center (crank angle 180 °) is a moderate length. Even when the stroke length of the slide 3 is changed, only the similar shape is changed, and the geometric shape of the diagram is not particularly changed. Since the crankshaft 8 in FIG. 6 has the slider 9 provided above, the crank angles at the top dead center and the bottom dead center are 180 ° and 0 °, respectively.

FIG. 7 shows the inclination angle 4 of the guide groove 25 when the stroke length of the slide 3 in FIG.
FIG. 9 is a mechanism explanatory view showing a mode in which a pin 23 of the drive link 11 moves along 4 ° 15 ′ in an easily understandable manner. The connection fulcrum 13 between the drive link 11 and the drive connection link 12 is connected to the connection fulcrum 13 ′, 1 at the top dead center and the bottom dead center of the slide 3.
3 on a straight line B connecting the three. The straight line B is the guide groove 25
Can be drawn according to the inclination angle of The swing angle C of the toggle upper link 6 changes according to the inclination angle of the guide groove 25, and the stroke length of the slide 3 changes.

FIG. 8 shows a third embodiment, in which the crankshaft 8
When a slider 9 that can freely move up and down is provided below and is driven via a connecting rod 10, the center connecting pin 7 between the toggle upper link 6 and the toggle lower link 4 is directly connected to the drive link 12 and the drive link 11. It is connected to the slider 9. The center of the gear 24 coincides with the position (23) occupied by the center of the pin 23 erected on the drive link 11 at the bottom dead center of the slide 3. The operation is the same as in the second embodiment.

FIG. 11A shows the stroke diagram of the slide 3 in the third embodiment, and FIG. 11B shows the relationship between the inclination angle of the guide groove 25 and the stroke length of the slide 3. As is clear from FIG. 11A, the stroke diagram draws a gentle curve in the vicinity of the top dead center, indicating that the acceleration due to the reversal of the slide 3 at the top dead center is small and can be adapted to high-speed driving. . In addition, it is almost the same as the second embodiment that the stop time at the bottom dead center is also moderately long, indicating that it has the characteristics of the press machine using the toggle link and can cope with high-speed operation. I have.

FIG. 9 shows a fourth embodiment, in which the crankshaft 8
A slider 9 is provided below the connecting rod 1
0, the slider 9 is moved up and down, and the center connecting pin 7 connecting the toggle upper link 6 and the toggle lower link 4 is connected.
Drive slider 11 and drive connection link 1
2 illustrates a case where the center of the pin 23 of the drive link 11 and the center O of the gear 24 in the bottom dead center state of the slide 3 are eccentric in the vertical direction by an eccentric amount E. Gear 24
The pin 23 is guided and constrained by a guide groove 25 provided on one diameter of the guide groove 25. When the inclination angle of the guide groove 25 is changed from 0 ° to, for example, 45 °, the connection between the drive link 11 and the drive connection link 12 is established. The fulcrum 13 moves to the connection fulcrum 13A at the bottom dead center position of the slide 3, that is, the lower end position of the slider 9 according to the eccentricity E, and the bottom dead center position of the slide 3 changes.

In FIG. 12B showing the relationship between the bottom dead center position of the slide 3 and the stroke length of the slide 3 and the inclination angle of the guide groove 25, the bottom dead center position of the slide 3 is F.
Only change. This is due to the appropriate eccentricity E
This indicates that the stroke length of the slide 3 can be adjusted by largely changing the inclination angle of the guide groove 25, and that the bottom dead center of the slide 3 can be finely adjusted by finely adjusting the inclination angle. The slide stroke diagram in the fourth embodiment shown in FIG. 12A is not much different from the above-described second and third embodiments, and the press machine according to the fourth embodiment can cope with high-speed operation, and It can be seen that it has the property of using a toggle link.

The first embodiment shown in FIG.
Is moved on an arc by the third link 18, so there is a slight difference from the case where the second to fourth embodiments are constrained to move on a straight line. The slide stroke diagram shown in FIG. 11 and the relationship between the inclination angle and the stroke length of the slide 3 are similar,
Detailed analysis comparisons are omitted. Slide 3
Also, when an appropriate amount of eccentricity is provided between the center of the connection fulcrum 13 and the center of the worm wheel 15 in the state of the bottom dead center, since it is similar to FIG. 12, the detailed comparison is omitted.

FIGS. 6 to 9 show the crankshaft 8.
The same result can be obtained when the same configuration is provided symmetrically to the left and right with respect to the vertical line passing through the center, and any one of the left and right or the symmetrical press machine can be used.

[0048]

As is apparent from the above description, according to the present invention, the change ratio of the stroke length of the slide by adjusting the inclination angle is as large as 8 to 10, and as is clear from the slide stroke diagram, The reversal acceleration at the top dead center is small, and it can cope with high-speed operation. The bottom dead center dwell time has a moderate length and has the characteristics of a press machine using a toggle link. It will not be lost even if you change it. In addition, the stroke length of the slide can be adjusted with the bottom dead center unchanged, and the bottom dead center can be finely adjusted, and the stroke length of the slide can be adjusted. Since the change of the stroke length of the slide and the fine adjustment of the bottom dead center are performed by adjusting the rotation angle of a gear or a worm wheel provided in a portion that does not affect the bottom dead center accuracy, it can be performed even during the pressing operation. Further, by providing the quick lift function, the condition inside the mold can be easily confirmed by inspecting the mold attached to the press machine, and the maintenance and inspection work can be improved.

Further, by fixing the stroke length adjusting mechanism during the press operation, the press load applied to the rotating means such as the worm wheel can be reduced. Therefore,
The size of the worm wheel and the like can be reduced, and the manufacturing cost can be reduced.

[Brief description of the drawings]

FIG. 1A is a front view of a main part of a press machine in a first embodiment. FIG. 1B is a three-dimensional view of a main part of a press machine in a first embodiment.

FIG. 2 is a three-dimensional view showing a connecting portion of a third link in the first embodiment.

3A is a sectional view taken along the line AA in FIG. 3B. FIG. 3B is a front view of a connecting portion of a third link in the first embodiment.

4A is a front view of a main part of a press machine according to a second embodiment. FIG. 4B is a three-dimensional view of a main part of the press machine according to a second embodiment.

FIG. 5 is an overall front view of a main part of a press machine according to a second embodiment.

FIG. 6 is a kinematic diagram of a driving mechanism according to a second embodiment.

FIG. 7 is an explanatory view of a driving mechanism in a second embodiment.

FIG. 8 is a kinematic diagram of a driving mechanism according to a third embodiment.

FIG. 9 is a kinematic diagram of a driving mechanism according to a fourth embodiment.

10A is a slide stroke diagram according to the second embodiment. FIG. 10B is a diagram illustrating a relationship between an inclination angle and a slide stroke according to the second embodiment.

11A is a slide stroke diagram according to a third embodiment; FIG. 11B is a diagram illustrating a relationship between an inclination angle and a slide stroke according to the third embodiment;

12A is a slide stroke diagram according to a fourth embodiment. FIG. 12B is a diagram illustrating a relationship between an inclination angle and a slide stroke according to the fourth embodiment.

[Explanation of symbols]

1 is a press machine, 2 is a point, 3 is a slide, 4 is a toggle lower link, 5 is a fixed fulcrum, 6 is a toggle upper link, 6A is an arm, 7 is a center connecting pin, 8 is a crankshaft, 8A is an eccentric part, 9 is a slider, 9A is a slider guide groove, 10 is a connecting rod, 11 is a drive link,
12 is a drive connection link, 13 is a connection fulcrum, 14 is a connection link, 15 is a worm wheel, 15A is a shaft, 15B is a jaw, 16 is a second arm, 17 is a second pin, and 18 is a third pin.
Link, 19 is a slide drive link, 20 is a second fixed fulcrum, 21 is a dynamic balance drive link, 22 is a dynamic balance weight, 23 is a pin, 24 is a gear, 25 is a guide groove, 26 is a pinion, and 27 is a plunger. , 28 are guides, 29 is a post, 30 is a post guide, 31 is a press machine, 31A
Is a frame, 32 is a bed, 34 is a slide adjustment device,
35 is a fixing cylinder, 36 is a worm shaft, 37A, 3
7B is a bush, 38 is an oil passage, and 40 is fixing means.

Claims (5)

[Claims] 1. A slider (9) that makes the rotational movement of a crankshaft (8) move up and down via a connecting rod (10), a drive link (11) connecting one end to the slider (9), and one end. And a drive connection link (12) connecting the drive connection (11) to the drive link (11), and one point of the member is swingably supported by a fixed fulcrum, and one end is connected to the drive connection link (12), and the other end is a link member. A toggle upper link (6) connected to the slide (3) via a link, a stroke length adjusting mechanism for restricting swinging motion of a fulcrum connecting the drive link (11) and the drive connection link (12), and A press machine characterized by having: 2. The stroke length adjusting mechanism comprises a connecting fulcrum standing on the drive link and a third link having one end connected to the connecting fulcrum.
And a shaft (1) rotatably supported by the frame (31A).
5A) and a second arm (1) having one end fixed to the shaft (15A) and the other end connected to the other end of the third link (18).
The press machine according to claim 1, further comprising: (6) a rotating unit configured to rotate the shaft (15A). 3. The rotator has a worm wheel (15) fixed to the shaft (15A) and a worm shaft (36) meshed with the worm wheel (15). The press machine according to claim 2. 4. The stroke length adjusting mechanism includes a shaft (15).
A) and a fixing means for fixing the fixing cylinder (3) movably fitted to the shaft (15A).
5) a jaw (15B) provided on the shaft (15A) for regulating the moving distance of the fixing cylinder (35); and a pressure oil between the jaw (15B) and the fixing cylinder (35). The press machine according to claim 2, further comprising: a pressurized oil supply device that supplies pressure. 5. The stroke length adjusting mechanism is provided with a pin (23) erected on the drive link (11) and a guide groove (25) into which the pin (23) is movably fitted. The press machine according to claim 1, further comprising a gear (24), and gear rotation angle adjusting means for adjusting a rotation angle of the gear (24).