JP2000343286A - Slide drive device of machine press - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a simple construction, easy maintenance/check/repair and a capability in high speed progressive working of a thick plate by arranging a pair of drive constituting parts consisting of a crank shaft, a connecting rod, upper/intermediate/lower/lateral links, etc., symmetrically in the left/right directions and driving a slide. SOLUTION: Crank shafts 12A, 12B are rotated, connecting rods 11A, 11B push/pull upper link arms 31A, 31B in the left/right directions of a press machine 1. Upper link arms 8A, 8B perform rock motion around first support pins 5A, 5B. The rocking motion is transmitted by intermediate links 6A, 6B to lateral links 4A, 4B as the oscillation motion around second support pins 7A, 7B. The center of second connecting pins 24A, 24B performs the motion on a locus (d), and lower links 3A, 3B and a slide 28 perform an elevation motion. Because drive constituting parts 2A, 2B are arranged symmetrically to the left/right, the movements of each member are in opposite directions to each other, and hence a press machine is dynamically balanced as a whole.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a slide drive for a mechanical press used for thick plate forging progressive processing.

[0002]

2. Description of the Related Art Conventionally, there are many slide driving devices for mechanical presses using a so-called link mechanism in which a gear and a lever are incorporated in a crank mechanism. A knuckle mechanism capable of outputting a large forming load especially near the bottom dead center has been used for cold forging with the aim of slowing down the slide at a relatively high position and enabling deep drawing. Also, in the thick plate forging progressive processing, the lowering speed of the slide over a wide range near the bottom dead center is required as the suppression of vibration and noise and the higher precision of the product are required due to the higher speed to improve productivity. However, those that are slow are regarded as advantageous and have been attracting attention.

Under these circumstances, as a conventional technique, there is a slide drive device that drives a symmetric double knuckle mechanism by a rotationally driven crankshaft, but a mechanism that converts the rotation of the crankshaft into a linear motion, that is, a linear mechanism. Is required, for example, as described in Japanese Patent Application Laid-Open No. 51-106278.
A Robert's approximate linear motion mechanism as disclosed in US Pat.

[0004]

SUMMARY OF THE INVENTION The above-mentioned JP-A-51-1
The linear mechanism of 06278 requires a plurality of pins and rods, and therefore has a complicated configuration. Since the linear mechanism is disposed between the crank and the knuckle mechanism, the distance between the guide rods connected to the knuckle mechanism becomes long. There is fear. When the distance between the guide rods is long in this way, warping is likely to occur due to the reaction force during processing,
Not only does the processing accuracy decrease, but the slides also have to be long, which inevitably increases the weight and complicates the configuration to deal with this, so if you spend a lot of time on maintenance, inspection and repair, In addition to workability,
There were many issues in terms of manufacturing costs.

Further, when high precision of the product is required, it is necessary to finely correct the position of the bottom dead center of the slide due to the temperature change of the machine or the mold. However, the screw at the point of the slide in the conventional knuckle mechanism is required. In the method of adjusting the bottom dead position of the slide by rotating the nut manually or in a predetermined direction by a motor, fine adjustment work is difficult, and a stable and accurate product cannot be obtained.

SUMMARY OF THE INVENTION It is an object of the present invention to solve the above-mentioned problems, to provide a mechanical press which has a simple structure, can be manufactured at a low cost, can be easily maintained, inspected and repaired, and can speed up a thick plate forging process. To provide a slide drive device.

[0007]

According to the first aspect of the present invention,
In a slide drive device of a mechanical press in which a slide moves up and down by a left drive component and a right drive component, the left drive component is provided on a left crankshaft rotatably supported by a crown portion and on the left crankshaft. A left gear, an upper left link swingably supported by a left first fulcrum pin provided on the crown portion, a left connecting rod connecting a base end to an eccentric portion of the left crankshaft, A left middle link connected by a left first connecting pin together with a distal end of the connecting rod and a lower end of an arm of the upper left link, a lower left link whose lower end is swingably connected to a left point, A left lateral link connected to a lower end of the middle left link and an upper end of the lower left link by a left second connecting pin, and a base end supported by a second fulcrum pin; Department is in front A slide drive device for a mechanical press, wherein the left drive component is disposed symmetrically with respect to the left and right centers of a right gear meshing with the left gear, and provided with members similar to the left drive component. .

In this invention, since the knuckle mechanism is of the opposing type, the operation of each member of the left and right drive components becomes symmetrical, and the left and right dynamic balance of the entire mechanical press can be achieved. In addition, by providing the crankshaft on each of the right and left sides, the configuration can be simplified and the manufacturing cost can be reduced.

According to a second aspect of the present invention, there is provided the slide driving device according to the first aspect, wherein the second fulcrum pin is provided with a moving means capable of moving in the left-right direction of the mechanical press.

In this invention, by moving the second fulcrum pin in the left-right direction of the mechanical press, the second connecting pin and the lower link connected to the second connecting pin move via the horizontal link. Then, the slide connected to the lower link lower end via the connection mechanism moves slightly. Therefore, in addition to the operation and effect of the first aspect, by performing this operation during the press operation, the bottom dead center can be finely corrected.

According to a third aspect of the present invention, the moving means includes:
3. The slide drive device according to claim 2, further comprising a cylinder, a rod in which the second fulcrum pin is engaged with the clevis at the tip, a fluid circuit under pressure control, and detection means for detecting a slide position. It is.

In this invention, in addition to the functions and effects of the invention described in claim 2, by using a cylinder for the moving means, a fluid can be used as a drive source. Here, by detecting the position of the slide using a slide position detecting device, for example, a linear scale, and controlling the pressure of the fluid based on the result, the second position is detected via the cylinder and the rod.
By moving the fulcrum pin, the position of the bottom dead center of the slide can be corrected.

According to a fourth aspect of the present invention, the moving means includes:
A case fixed to the crown portion, a worm wheel provided in the case, a worm shaft engaged with the worm wheel and driven by a motor, and a screw portion provided at one end portion is screwed with the worm wheel. 3. The slide drive device according to claim 2, wherein a screw shaft is provided for engaging the other end with the second fulcrum pin.

In this invention, in addition to the function and effect of the second aspect of the invention, the position of the bottom dead center of the slide is corrected by using a motor as a drive source of the moving means and controlling the rotation angle of the motor. can do.

According to a fifth aspect of the present invention, the left and right crankshafts are provided with a crankshaft weight portion having a center of gravity in a direction that is substantially 180 ° out of phase with the crankshaft eccentric portion. 1. The slide drive device according to 1.

In this invention, in addition to the functions and effects of the first aspect of the present invention, it is possible to remove the imbalance of the mechanical press due to the eccentric portion when the crankshaft rotates and the inertia force of the connecting rod connected to the eccentric portion. it can.

According to a sixth aspect of the present invention, the left gear and the right gear engage with the rim portion and the arm portion of the gear and have a center of gravity in a direction substantially 180 ° out of phase with the eccentric portion of the crankshaft. The slide drive device according to claim 1, further comprising a weight portion.

In this invention, in addition to the functions and effects of the first aspect, it is possible to eliminate imbalance of the mechanical press due to the eccentric portion when the crankshaft rotates and the inertia force of the connecting rod connected to the eccentric portion. Can be.

According to a seventh aspect of the present invention, the left lateral link and the right lateral link are provided on the second fulcrum pin side extension of an axis connecting the axis of the second fulcrum pin and the second connecting pin. 2. An extension part having two fulcrum pins as a fulcrum, and a balance weight which is connected to the extension part by a third connecting pin and which moves up and down in opposition to the elevation of the lower link is provided. It is a slide drive device of description.

In this invention, since the balance weight faces the vertical movement of the slide, the inertial force generated by the vertical movement of the slide can be canceled. That is, in addition to the first aspect of the present invention, a dynamic balance in the vertical direction of the press machine can be obtained, thereby reducing vibration and noise and improving the working environment.

[0021]

FIG. 1 shows a first embodiment of the present invention. In the figure, the state when the slide 28 is at the bottom dead center is indicated by a solid line, and the state when the slide 28 is at the top dead center is indicated by a two-dot chain line.

In FIG. 1, a press machine 1 includes a crown 30, columns 26A and 26B, a slide 28, and a bed 2.
9, a bolster 25, and a drive component 2A, which is symmetrical and includes a knuckle mechanism, inside the crown 30.
2B are provided.

A main motor 18 serving as a power source is provided above the crown 30, and a pulley 19 is provided on a drive shaft of the main motor 18. A belt 13 is wound around the pulley 19 and a flywheel 17 provided at one end of the crankshaft 12A, and the rotational energy stored in the flywheel 17 is transmitted to the crankshaft 12A. On the other hand, the gear 14A is the gear 1 of the right drive component 2B.
4B.

The gears 14A and 14B are fixedly mounted on the crankshafts 12A and 12B rotatably supported by the crown 30, respectively. Eccentric part 10 of crankshafts 12A and 12B
The proximal ends of the connecting rods 11A and 11B are connected to A and 10B, respectively.

On the other hand, above the crown 30, the crown 3
The first fulcrum pins 5A and 5B supported by the first fulcrum 0 are provided. The upper links 8A, 8B are swingably supported by the first fulcrum pins 5A, 5B, respectively. The arms 31A, 31B of the upper links 8A, 8B are connected to the distal ends of the connecting rods 11A, 11B and the upper ends of the middle links 6A, 6B by first connecting pins 23A, 23B, respectively. Middle link 6
A, 6B, together with the upper ends of the lower links 3A, 3B and the tips of the lateral links 4A, 4B, together with the second connecting pins 24A,
24B. The brackets 9A and 9B fixed to the outer surface of the crown 30, respectively,
A and 4B are connected to the base end portions by second fulcrum pins 7A and 7B, respectively.

The slide 28 is vertically slidably guided by a slide guide 20 fixed to the columns 26A and 26B. The slide 28 includes connecting mechanisms 32A, 32A having a function of adjusting the die height H.
B is provided. The lower ends of the ball shapes of the lower links 3A and 3B are respectively connected via the coupling mechanisms 32A and 32B.
It is connected to the slide 28.

When the main motor 18 starts, the pulley 1
9. The flywheel 17 rotates via the belt 13. The rotational force of the flywheel 17 is applied to the crankshaft 12 by connecting / disconnecting a clutch brake (not shown).
A, and the torque is transmitted to the gears 14A, 14B.
Is transmitted to the crankshaft 12B. The rotation of the crankshafts 12A, 12B causes the connecting rods 11A, 11B
Pushes and pulls the arms 31A and 31B in the left-right direction of the press machine 1. Therefore, the upper links 8A and 8B perform a swinging movement about the first fulcrum pins 5A and 5B. The oscillating motion is performed by the middle links 6A and 6B by the lateral links 4A and 4B.
Is transmitted as a swinging motion about the second fulcrum pins 7A and 7B. The swinging motion causes the second connecting pin 24
The centers of A and 24B make a motion as shown in a trajectory d.
Therefore, the lower links 3A and 3B and the slide 28 perform a vertical movement.

At this time, since the lower link 3A, 3B raises and lowers the slide 28 while maintaining a substantially vertical state, the parallelism between the slide 28 and the bolster 25 at the time of raising and lowering the slide 28 is stabilized, and the slide 28 is moved at the time of raising and lowering. The thrust force acting on the guiding slide guide 20 can be greatly reduced.

During operation of the press machine 1, the crankshaft 12
In order to balance the inertial force of the eccentric portions 10A and 10B when the A and B rotate, the crankshaft weights 27A and 27B on the crankshafts 12A and 12B and / or the gear weights 21A on the gears 14A and 14B. 21B, respectively.

The arms 31A, 3 of the upper links 8A, 8B
1B has connecting rods 11A and 11B and middle links 6A and 6
It takes weight such as B. For this reason, when the upper links 8A, 8B perform a swinging movement about the first fulcrum pins 5A, 5B, an inertial force acts on the upper links 8A, 8B. In order to balance the inertial force, upper link weight portions 22A and 22B are provided on the opposite sides of the arms 31A and 31B, respectively.

Drive components 2A and 2B for performing the above-described operations
Is provided symmetrically with respect to the press machine 1 so that the operations of members such as the gears 14A and 14B and the crankshafts 12A and 12B are in opposite directions.
It is possible to achieve a dynamic balance as a whole.

Next, FIG. 2 shows a second embodiment of the present invention.
FIG. 2 shows an opposed type in which the bracket 9A is replaced with a bottom dead center correcting device 33A in the left driving component 2A in FIG. 1 and the bottom dead center correcting device is similarly provided in the right driving component. 2 shows a cross section of a main part of a left driving component 2A of a press machine 1 having a knuckle mechanism.

In the present embodiment, the center of the second fulcrum pin 7A is located at O7 and the slide 28 is at the bottom dead center. When the center is moved to O7a, the lower link 3A,
The state of the horizontal link 4A, the middle link 6A, and the slide 28 is shown, and the state before the movement of the second fulcrum pin 7A is shown by a solid line, and the state after the movement is shown by a two-dot chain line.

The bottom dead center correction device 33A includes a servo cylinder 34A directly attached to the column 26A of the press machine 1,
The servo cylinder 34A is connected to the second fulcrum pin 7A via a clevis 36A attached to the tip of a rod 35A of the servo cylinder 34A.

Based on a slide position signal of a linear encoder comprising a scale 37 erected on the bed 29 and a detector 38 attached to the slide 28, a signal from a servo valve controlled by a signal from a servo controller (not shown) is used. When the rod 35A of the servo cylinder 34A moves by a predetermined stroke due to the fluid pressure, the servo cylinder 34A
When the center of the second fulcrum pin 7A moves from O7 to O7a in synchronization with the operation stroke amount of A, the center of the second connection pin 24A of the lower link 3A and the middle link 6A connected together with the horizontal link 4A is From O4 to O4a, the slide 28 rises by D, and the bottom dead center position is finely corrected.

In the second embodiment, a servo cylinder is used as a drive source of the bottom dead center correction device. However, the present invention can be implemented by replacing the cylinder with another cylinder.

Next, FIG. 3 shows a third embodiment of the present invention. FIG. 3 is a diagram in which the bracket 9A is replaced with a bottom dead center correction device 40A in the left driving component 2A in FIG.
Similarly, a cross section of a main part of the left driving component 2A of the press machine 1 having the opposed knuckle mechanism provided with the bottom dead center correction device is shown in the right driving component.

In the present embodiment, the center of the second fulcrum pin 7A is located at O7 and the bottom dead center correction device 40A is operated from the state where the slide 28 is at the bottom dead center to move the center of the second fulcrum pin 7A. Lower link 3A, horizontal link 4 when moving to O7a
A, the state of the middle link 6A, and the slide 28 are shown, and the state before the movement of the second fulcrum pin 7A is shown by a solid line, and the state after the movement is shown by a two-dot chain line.

The bottom dead center correction device 40A includes a case 41A fixed to the column 26A of the press machine 1,
1A, a worm wheel 42A provided therein, a worm shaft 43A driven by a brake motor 44A engaged with the worm wheel 42A, a screw portion provided at one end is screwed to the worm wheel 42A, and the other end is connected to the second. Support pin 7A
And a screw shaft 45A connected to the shaft.

By rotating the worm shaft 43A and the worm wheel 42A forward / reversely using the brake motor 44A as a power source, the screw shaft 45A screwed with the worm wheel 42A is moved by a required dimension in the horizontal direction. When the center of the second fulcrum pin 7A connected to the screw shaft 45A moves from O7 to O7a, the center of the second connection pin 24A of the lower link 3A and the middle link 6A connected together with the horizontal link 4A becomes O4. To O4a, the slide 28 rises by D, and the bottom dead center position is finely corrected.

The rotation angle of the motor shaft of the brake motor 44A is measured by a rotary encoder (not shown) attached to the worm shaft 43A, and the measured rotation angle is feedback-controlled. Although the power source of this embodiment is a brake motor, a servo motor, a stepping motor, a geared motor, or the like may be used as the power source.

Next, FIG. 4 shows a fourth embodiment of the present invention. FIG. 4 shows the left drive component 2A in FIG.
The second fulcrum pin 7A and the second connecting pin 24 are attached to the horizontal link 4A.
A on the second fulcrum pin side extension of the axis connecting the axis with A
Third connection of a horizontal link 51A having an extension 55A with the fulcrum pin 7A as a fulcrum and a balance weight 53A guided slidably up and down by a balance weight guide 54A to the extension 55A of the horizontal link 51A. Pin 52A
, And the horizontal drive 51A is similarly connected to the right drive component.
The third connecting pin 52A, the balance weight guide 54A,
The main part cross section of 2 A of left driving components of the press machine 1 which has the opposed knuckle mechanism provided with the balance weight 53A is shown. In the drawing, the state when the slide 28 is at the bottom dead center is indicated by a solid line, and the state when the slide 28 is at the top dead center is indicated by a two-dot chain line.

The horizontal link 51A uses the second fulcrum pin 7A as a fixed fulcrum, and the second link pin 24A and the third link pin 52A.
A has a movable fulcrum. Therefore, the balance weight 53A
Is moved in a direction opposite to the direction in which the slide 28 is moved up and down. Therefore, the vertical inertial force of the slide 28 can be removed by the balance weight 53A and the right balance weight (not shown).

In the first to fourth embodiments, the rotational force of the flywheel is directly transmitted to the crankshaft. However, a gear may be provided between the flywheel and the crankshaft. 1
FIG. 5 shows an embodiment in the case of performing the step deceleration.

Drive shaft 15 engaged with flywheel 17
Is provided with a pinion 16, and the pinion 16
Meshes with 4A. The gear 14A also meshes with the gear 14B, so that the rotational force of the flywheel 17 is transmitted to the left drive mechanism 2A and the right drive mechanism 2B. Naturally, in this case, the same effects as those of the first to fourth embodiments can be obtained.

[0046]

As is apparent from the above description, according to the present invention, the inclination angle of the lower link for raising and lowering the slide is made very small, and no thrust force is generated on the slide, so that the lower link has a higher position on the lower dead center. The opposing knuckle mechanism that can mold high-precision products even in extrusion processing where molding starts from
Dynamic balance can be achieved by providing balance weights everywhere. In addition, since two crankshafts are provided, the configuration can be simplified, so that manufacturing costs can be reduced.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a press machine according to a first embodiment.

FIG. 2 is a longitudinal sectional view of a main part of a press machine according to a second embodiment.

FIG. 3 is a longitudinal sectional view of a main part of a press machine according to a third embodiment.

FIG. 4 is a longitudinal sectional view of a main part of a press machine according to a fourth embodiment.

FIG. 5 is a longitudinal sectional view of the press machine when the speed is reduced by one step.

[Explanation of symbols]

1 is a press machine, 2A and 2B are drive components, 3A and 3B
Is the lower link, 4A and 4B are the horizontal links, 5A and 5B are the first links
A fulcrum pin, 6A and 6B are middle links, 7A and 7B are second fulcrum pins, 8A and 8B are upper links, 9A and 9B are brackets, 10A and 10B are crankshaft eccentric parts, 11A and 11
B is a connecting rod, 12A and 12B are crankshafts, 13 is a belt, 14A and 14B are gears, 15 is a drive shaft, 16 is a pinion, 17 is a flywheel, 18 is a main motor, 19 is a pulley, 20 is a slide guide, 2
1A and 21B are gear weight portions, 22A and 22B are upper link weight portions, 23A and 23B are first connecting pins, 24
A and 24B are second connection pins, 25 is a bolster, 26A,
26B is a column, 27A and 27B are crankshaft weights, 28 is a slide, 29 is a bed, 30 is a crown,
31A and 31B are upper link arms, 32A and 32B are coupling mechanisms, 33A is a bottom dead center correction device, 34A is a servo cylinder, 35A is a rod, 36A is a clevis, 37 is a scale, 38 is a detector, and 40A is a lower part. Dead point correction device, 41A
Is a case, 42A is a worm wheel, 43A is a worm shaft, 44A is a brake motor, 45A is a screw shaft, 51
A is a horizontal link, 52A is a third connecting pin, 53A is a balance weight, 54A is a balance weight guide, 55A.
Is an extension.

Claims (7)

[Claims] 1. A slide drive device of a mechanical press in which a slide moves up and down by a left drive component and a right drive component, wherein the left drive component comprises a left crankshaft rotatably supported by a crown, and the left crankshaft. A left gear provided on a crankshaft, an upper left link swingably supported by a left first fulcrum pin provided on the crown portion, and a left connectin connecting a base end portion to an eccentric portion of the left crankshaft A rod, a left middle link connected by a left first connection pin together with a distal end of the left connecting rod and a lower end of an arm of the upper left link, and a lower end swingably connected to the left point. A lower left link and a left lateral link having a distal end connected to a lower end of the middle left link and an upper end of the lower left link by a second left connecting pin, and a base end supported by a second fulcrum pin. , The right side drive The component press is characterized in that the left drive component is disposed symmetrically with respect to the left and right center of the right gear meshing with the left gear with the same member as the left drive component. Slide drive. 2. A slide drive device according to claim 1, wherein said second fulcrum pin is provided with a moving means capable of moving in the left-right direction of a mechanical press. 3. The moving means includes a cylinder, a rod in which a second fulcrum pin is engaged with a clevis at a tip, a fluid circuit under pressure control, and a detecting means for detecting a slide position. The slide drive device according to claim 2, wherein 4. The moving means is provided at one end of a case fixed to the crown portion, a worm wheel provided in the case, a worm shaft engaged with the worm wheel and driven by a motor. 3. The slide drive device according to claim 2, wherein a screw shaft is provided, the screw portion being screwed to the worm wheel and the other end portion being engaged with the second fulcrum pin. 5. The slide drive device according to claim 1, wherein the left and right crankshafts are provided with a crankshaft weight portion having a center of gravity in a direction substantially 180 ° out of phase with the crankshaft eccentric portion. . 6. The left gear and the right gear are engaged with a rim portion and an arm portion of the gear and substantially coincide with the eccentric portion of the crankshaft.
2. The slide drive device according to claim 1, further comprising a gear weight portion having a center of gravity in directions different in phase by 0 [deg.]. 7. The left lateral link and the right lateral link are provided with the second fulcrum pin as a fulcrum on an extension of an axis connecting the second fulcrum pin and the second connecting pin on the second fulcrum pin side. 2. A slide drive according to claim 1, wherein a dynamic balance weight is provided which is connected to the extension by a third connecting pin and which moves up and down in opposition to the elevation of the lower link. apparatus.