JP5303922B2 - Variable motion link press and its motion switching method - Google Patents

Description

  The present invention relates to a variable motion link press capable of changing a slide motion and a motion switching method thereof.

As a mechanical press for forming a metal plate into a predetermined shape with a mold, an eccentric mechanical press, a link mechanical press, a servo press, and the like are known.
The eccentric mechanical press and the link mechanical press are press devices that use a flywheel driven by an electric motor as a power source and convert the rotational motion of the flywheel into a slide motion by an eccentric shaft or a link mechanism.
The servo press is a press device in which the drive motor is a servo motor, there is no flywheel, and the crank mechanism or link mechanism is driven by the servo motor.

  The mechanical press mentioned above is disclosed by patent document 1, 2, for example.

Patent document 1 aims at the quick return mechanism of the link press which relieves the impact force added to a pin.
Therefore, this link press is a link press in which an eccentric ring 64 and a slide 52 of a main eccentric gear 56 rotating around a main shaft 55 are pin-joined by a main link 59 and a connecting rod 60, as shown in FIG. In the quick return mechanism, the main eccentric gear 56 has a small gear 63 smaller than the driving main gear 62, a sub-excentric gear 58 that rotates about the intermediate shaft 57 is provided, and the sub-gear 65 of the sub-excentric gear 58 is moved to the small gear. The sub link 61 is engaged with the eccentric wheel 66 of the sub eccentric gear 58 and the main link 59, and the pin 67 connecting the main link 59 and the sub link 61 is elliptically circulated. It draws a trajectory.

Patent Document 2 aims at a slide drive mechanism of a servo press that has a high degree of freedom in arrangement and selection of actuators and that allows easy setting of press characteristics.
Therefore, as shown in FIG. 17, the toggle mechanism 70 in this slide drive mechanism includes a first link 72 and a second link 74 that are axially attached to each other, and a driving force of the actuator 71 that is axially attached to the first link 72. Is provided to the first link 72. The other end of the first link 72 is pivotally attached to a part of the crown 73 of the servo press. The other end of the second link 74 is pivotally attached to the slide 75. The first link 72 has a shaft landing point (power input point 78) with the drive link 76 at a site different from the shaft landing point (power output point 77) with the second link 74.

JP 2002-178192 A, "Link press quick return mechanism" JP 2007-203360 A, “Slide Drive Mechanism of Servo Press”

Of the mechanical presses described above, the slide motions of the eccentric mechanical press and the link mechanical press are fixed and cannot be varied. Here, “slide motion” means a motion of the slide, that is, a time history of the slide position with respect to the stationary system.
In this slide motion, the lower side 1/3 to 1/4 of the stroke is the forming region, and it is sufficient that this is a low speed in the narrowing forming. The rest is a moving area, which is used for loading / unloading materials / products.

  The EXCEN mechanical press has a fixed slide motion, so that the speed of the forming area is high, and it is not suitable for drawing forming that requires a low speed in the forming area. In addition, the link machine press has a problem of low productivity because the speed of the forming region is low.

  Also, the servo press can change the slide motion by the acceleration / deceleration of the servo motor, but there is an energy loss that does not contribute to molding during the acceleration / deceleration of the servo motor. In addition, since there is no flywheel, the power supply and motor are increased in size and cost.

  Furthermore, since the link press of Patent Document 1 uses a link with three nodes (three-node link), it is difficult to precisely manage and manufacture the relative position of the three nodes, and the bending force acts on the link. There is a point.

  The present invention has been developed to solve the above-described problems. That is, an object of the present invention is to provide a variable motion link press capable of changing a slide motion without increasing the size and cost of a power source / motor and preventing a bending force from acting on the link, and a method for switching the motion. There is to do.

According to the present invention, the upper link is attached to the lower surface of the slide, and the lower end of the upper link is rotatably attached to the first node and extends upward.
A second link having a lower end rotatably attached to the upper end of the first link at a second node and extending upward;
A third link with a lower end rotatably attached to the upper end of the first link at the second node and extending obliquely upward;
A first eccentric drive shaft that is located vertically above the first node and that eccentrically moves the third node at the upper end of the second link with a constant first eccentric amount;
A second eccentric drive shaft that eccentrically moves the fourth node of the upper end portion of the third link with a constant second eccentric amount;
A drive device that rotationally drives the first eccentric drive shaft and the second eccentric drive shaft;
The drive, possess the first eccentric drive shaft and the phase difference of the second eccentric drive shaft, the direction of rotation, a variable mechanism capable of adjusting the rotational speed difference,
The variable mechanism can arbitrarily set a phase difference between the first eccentric drive shaft and the second eccentric drive shaft, and the speed of the second eccentric drive shaft is switched between constant speed and double speed with respect to the first eccentric drive shaft. There is provided a variable motion link press characterized in that it is possible and the direction of rotation can be switched in the same direction or in the opposite direction .

According to a preferred first embodiment of the present invention, the driving device includes a first motor, a first flywheel, and a first clutch and brake for driving the first eccentric drive shaft to rotate.
A second motor, a second flywheel, and a second clutch and brake for rotationally driving the second eccentric drive shaft;
A transmission mechanism, a forward / reverse switching mechanism, and a third clutch are provided to connect between the first eccentric drive shaft and the second eccentric drive shaft.

According to a second preferred embodiment of the present invention, the drive device comprises: a first motor, a first flywheel, and a first clutch and brake for rotationally driving the first eccentric drive shaft;
A second motor, a second flywheel, and a second clutch and brake for rotationally driving the second eccentric drive shaft;
A synchronization control system for controlling synchronization between the first motor and the second motor;

According to a third preferred embodiment of the present invention, the drive device comprises: a first motor, a first flywheel, and a first clutch and brake for driving the first eccentric drive shaft to rotate;
The first flywheel has a speed change mechanism, a forward / reverse switching mechanism, and a second clutch and brake for rotationally driving the second eccentric drive shaft.

According to a fourth preferred embodiment of the present invention, the drive device comprises: a first motor, a first flywheel, and a first clutch and brake for driving the first eccentric drive shaft to rotate;
A servo motor for rotationally driving the second eccentric drive shaft;
A synchronization control system for controlling synchronization between the first motor and the servo motor;

Further, according to the present invention, the upper link is attached to the lower surface, and the first link that is attached to the slide that vertically moves up and down is rotatably attached at the first node and extends upward,
A second link having a lower end rotatably attached to the upper end of the first link at a second node and extending upward;
A third link with a lower end rotatably attached to the upper end of the first link at the second node and extending obliquely upward;
A first eccentric drive shaft that is located vertically above the first node and that eccentrically moves the third node at the upper end of the second link with a constant first eccentric amount;
A second eccentric drive shaft that eccentrically moves the fourth node of the upper end portion of the third link with a constant second eccentric amount;
A drive device that rotationally drives the first eccentric drive shaft and the second eccentric drive shaft;
The phase difference between the first eccentric drive shaft and the second eccentric drive shaft is set, the speed of the second eccentric drive shaft is switched to the constant speed or double speed with respect to the first eccentric drive shaft, and the rotation direction is the same direction. Alternatively , there is provided a motion switching method of a variable motion link press characterized by switching in the reverse direction .

According to the apparatus and method of the present invention, the drive device has the variable mechanism that can adjust the phase difference, the rotational direction, and the rotational speed difference between the first eccentric drive shaft and the second eccentric drive shaft. Without using a servo motor, the phase difference between the first eccentric drive shaft and the second eccentric drive shaft is set, the speed of the second eccentric drive shaft is switched to the constant speed or double speed with respect to the first eccentric drive shaft, and It was confirmed by a simulation described later that at least four slide motions can be changed by switching the rotation direction to the same direction or the reverse direction.
Further, it has been confirmed by simulation described later that the production can be continued only with the first eccentric drive shaft even when the second eccentric drive shaft does not operate due to motor damage or the like.

Therefore, productivity can be maximized by changing the slide motion for each mold.
Moreover, since the speed of the 1st eccentric drive shaft and the 2nd eccentric drive shaft in a press cycle is constant speed, it can drive with a small size motor and a flywheel. Therefore, an expensive servo motor can be dispensed with.

  Further, the three links (first link, second link, and third link) constituting the apparatus of the present invention are links each having only two nodes (two-node links), and can be easily manufactured. Bending force does not act on

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the common part in each figure, and the overlapping description is abbreviate | omitted.

FIG. 1 is an overall configuration diagram of a variable motion link press according to the present invention.
In this figure, the variable motion link press 10 of the present invention includes a first link 12, a second link 14, a third link 16, a first eccentric drive shaft 22, a second eccentric drive shaft 24, and a drive device 30.

In this figure, reference numeral 1 denotes a slide which is attached to the lower surface with an upper mold (not shown) and moves up and down vertically. A lower mold (not shown) is installed below the slide 1, and a metal plate is sandwiched and pressed between the lower mold and the upper mold, and is molded into a predetermined shape by the mold. ing.
The vertical movement of the slide 1 may be performed in synchronization with two variable motion link presses 10, a combination of one variable motion link press 10 and a slide guide, or other means.

The first link 12 is a two-node link that is attached to the above-described slide 1 so that its lower end portion is rotatably attached to the first node 13 and extends upward.
The second link 14 is a two-node link that is attached to the upper end portion of the first link 12 so that the lower end portion is rotatably attached to the second node 15 and extends upward.
The third link 16 is a two-node link that is attached to the upper end portion of the first link 12 so that the lower end portion is rotatably attached to the second node 15 and extends obliquely upward.

The first eccentric drive shaft 22 is located vertically above the first node 13. The first eccentric drive shaft 22 is a crankshaft or an eccentric shaft that eccentrically moves the third node 17 at the upper end of the second link 14 with a constant first eccentric amount.
The second eccentric drive shaft 24 is located obliquely above the first node 13. The second eccentric drive shaft 24 is a crankshaft or an eccentric shaft that eccentrically moves the fourth node 18 at the upper end of the third link 16 with a constant second eccentric amount.

The drive device 30 is a drive device that rotationally drives the first eccentric drive shaft 22 and the second eccentric drive shaft 24. The drive device 30 also has a variable mechanism that can adjust the phase difference, rotation direction, and rotation speed difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24.
In this variable mechanism, the phase difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24 can be arbitrarily set, and the speed of the second eccentric drive shaft 24 with respect to the first eccentric drive shaft 22 is constant and double speed. The rotation direction can be switched to the same direction or the reverse direction. Details of the variable mechanism will be described later.

In the example of FIG. 1, the distance between the nodes of the first link 12 (the distance between the first node 13 and the second node 15) is 1000 mm, and the distance between the nodes of the second link 14 (the distance between the second node 15 and the third node 17). ) Is set to 1000 mm, and the distance between the nodes of the third link 16 (the distance between the second node 15 and the fourth node 18) is set to 1250 mm.
The eccentric amount of the first eccentric drive shaft 22 (distance between the shaft center and the third node 17) is 300 mm, and the eccentric amount of the second eccentric drive shaft 24 (distance between the shaft center and the fourth node 18) is 200 mm. The horizontal distance between the eccentric drive shaft 22 and the second eccentric drive shaft 24 is set to 1000 mm, the vertical distance is set to 700 mm, and the second eccentric drive shaft 24 is located below the first eccentric drive shaft 22.

Hereinafter, in this figure, the counterclockwise rotation is the forward rotation, the clockwise rotation is the reverse rotation, and the angles of the third node 17 and the fourth node 18 from the vertical axis are the press angles θ1 and θ2, respectively.
In FIG. 1, the press angle θ1 is 180 degrees, the press angle θ2 is 231 degrees, and the slide 1 is at the bottom dead center.

  2A and 2B are schematic diagrams showing a first slide motion of the variable motion link press 10 according to the present invention, in which FIG. 2A shows the bottom dead center of the slide 1 and FIG. 2B shows the top dead center.

  FIG. 2A is the same as FIG. 1. At the bottom dead center, the press angle θ1 is set to 180 degrees and the press angle θ2 is set to 231 degrees. The first eccentric drive shaft 22 and the second eccentric drive shaft 24 are Forward rotation at constant speed. Hereinafter, this first slide motion is referred to as “standard motion” or “exen motion”.

  2B, the press angle θ1 is 357 degrees, the press angle θ2 is 47 degrees, and the stroke of the slide 1 is approximately 772.4 mm.

FIG. 3 is an operation diagram of the first slide motion (standard motion). In this figure, the horizontal axis represents the press angle θ1 of the first eccentric drive shaft 22, and the vertical axis represents the stroke [mm] of the slide 1.
From this figure, it can be seen that the first slide motion (standard motion) is a general eccentric motion having a press angle of 180 degrees as a symmetry axis.

  4A and 4B are schematic diagrams showing a second slide motion of the variable motion link press 10 according to the present invention, where FIG. 4A shows the bottom dead center of the slide 1 and FIG. 4B shows the top dead center.

FIG. 4A is the same as FIG. 1 and differs from the first slide motion only in that the first eccentric drive shaft 22 rotates forward and the second eccentric drive shaft 24 rotates reversely.
That is, at the bottom dead center, the press angle θ1 is set to 180 degrees and the press angle θ2 is set to 231 degrees, and the first eccentric drive shaft 22 and the second eccentric drive shaft 24 rotate at a constant speed. Hereinafter, this second slide motion is referred to as “deep drawing motion”.

  At the top dead center of FIG. 4B, the press angle θ1 is 325 degrees, the press angle θ2 is 86 degrees, and the stroke of the slide 1 is about 858.4 mm.

FIG. 5 is an operation diagram of the second slide motion (deep drawing motion). In this figure, the horizontal axis represents the press angle θ1 of the first eccentric drive shaft 22, and the vertical axis represents the stroke [mm] of the slide 1.
From this figure, it can be seen that the second slide motion (deep drawing motion) is not symmetrical with respect to the press angle of 180 degrees, and is slow in the forming region of 90 to 180 degrees, and is therefore suitable for drawing.

  6A and 6B are schematic views showing a third slide motion of the variable motion link press 10 according to the present invention, in which FIG. 6A shows the bottom dead center of the slide 1 and FIG. 6B shows the top dead center.

FIG. 6A is the same as FIG. 1 and is different from the first slide motion only in that the first eccentric drive shaft 22 is forwardly rotated and the second eccentric drive shaft 24 is reversely rotated and double speed.
That is, at the bottom dead center, the press angle θ1 is set to 180 degrees and the press angle θ2 is set to 231 degrees. Hereinafter, this third slide motion is referred to as “deep drawing + fast return motion”.

  At the top dead center of FIG. 6B, the press angle θ1 is 267 degrees, the press angle θ2 is 61 degrees, and the stroke of the slide 1 is about 674.3 mm.

FIG. 7 is an operation diagram of the third slide motion (deep drawing + fast return motion). In this figure, the horizontal axis represents the press angle θ1 of the first eccentric drive shaft 22, and the vertical axis represents the stroke [mm] of the slide 1.
From this figure, the third slide motion (deep drawing + fast return motion) is not symmetric with respect to the press angle of 180 degrees, and is slow in the forming region of 90 to 180 degrees, so that it is suitable for drawing and 180 to 270. It can be seen that it is a fast-return motion that becomes faster at higher speeds.
In addition, since the slide almost stops near the top dead center between 270 and 60 degrees, the product is carried out and the material is carried in during this time, so that the production can be continued without operating the clutch / brake.・ Brake operation time loss is eliminated and productivity is increased, and clutch and brake wear is eliminated, and maintenance costs are improved.

  FIG. 8 is a schematic diagram showing the fourth slide motion of the variable motion link press 10 according to the present invention, where (A) shows the bottom dead center of the slide 1 and (B) shows the top dead center.

FIG. 8A is the same as FIG. 1 and is different from the first slide motion only in that the first eccentric drive shaft 22 is reversely rotated and the second eccentric drive shaft 24 is reversely rotated and double speed.
In this example, the press angle θ1 is set to 158 degrees and the press angle θ2 is set to 46 degrees at the bottom dead center. Hereinafter, this fourth slide motion is referred to as “low-speed touch motion”.

  At the top dead center in FIG. 8B, the press angle θ1 is 351 degrees, the press angle θ2 is 72 degrees, and the stroke of the slide 1 is about 787.0 mm.

FIG. 9 is an operation diagram of the fourth slide motion (low-speed touch motion). In this figure, the horizontal axis represents the press angle θ1 of the first eccentric drive shaft 22, and the vertical axis represents the stroke [mm] of the slide 1.
From this figure, the fourth slide motion (low-speed touch motion) is 200 mm above the bottom dead center and becomes low at the start of the molding area, so that the upper and lower molds can be contacted at low speed, reducing vibration and noise, There is an effect of improving molding quality. Moreover, since the speed is again increased after touching the mold, the production speed is not impaired. Furthermore, by adjusting the phase difference, it is possible to cope with a deep aperture to a shallow aperture by changing the timing of the low speed.

  FIG. 10 is a schematic diagram showing a fifth slide motion of the variable motion link press 10 according to the present invention, where (A) shows the bottom dead center of the slide 1 and (B) shows the top dead center.

FIG. 10A is the same as FIG. 1 and is different from the first slide motion only in that the second eccentric drive shaft 24 is stopped.
That is, at the bottom dead center, the press angle θ1 is set to 180 degrees, the press angle θ2 is set to 231 degrees, and only the first eccentric drive shaft 22 rotates at a constant speed. Hereinafter, this fifth slide motion is referred to as “1 motor stop motion”.

  At the top dead center of FIG. 10B, the press angle θ1 is 353 degrees, the press angle θ2 remains stopped at 231 degrees, and the stroke of the slide 1 is about 609.2 mm.

FIG. 11 is an operation diagram of the fifth slide motion (1 motor stop motion). In this figure, the horizontal axis represents the press angle θ1 of the first eccentric drive shaft 22, and the vertical axis represents the stroke [mm] of the slide 1.
From this figure, it can be seen that the fifth slide motion (one motor stop motion) is a general eccentric motion having a press angle of 180 degrees as a symmetry axis.

  According to the above-described device of the present invention, the drive device 30 has the variable mechanism that can adjust the phase difference, the rotational direction, and the rotational speed difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24. Accordingly, the phase difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24 is set without using a servo motor, and the speed of the second eccentric drive shaft 24 is made constant with respect to the first eccentric drive shaft 22 or By switching to the double speed and switching the rotation direction to the same direction or the reverse direction, it is possible to change to the above-described first to fourth slide motions.

  Even when the second eccentric drive shaft 24 does not operate due to motor damage or the like, the first eccentric drive shaft 22 alone can be used to change to the fifth slide motion described above, and production can be continued.

  FIG. 12 is a diagram illustrating a first embodiment of the drive device 30. In this figure, the drive device 30 includes a first motor 32A, a first flywheel 34A, and a first clutch and brake 36A connected in series, a second motor 32B, a second flywheel 34B connected in series, It has a second clutch & brake 36B, a transmission mechanism 38, a forward / reverse switching mechanism 37, and a third clutch 39.

  The first motor 32A, the first flywheel 34A, and the first clutch & brake 36A rotate the first eccentric drive shaft 22. The second motor 32B, the second flywheel 34B, and the second clutch & brake 36B rotate the second eccentric drive shaft 24.

Further, the speed change mechanism 38, the forward / reverse switching mechanism 37 and the third clutch 39 connect the first eccentric drive shaft 22 and the second eccentric drive shaft 24. With the third clutch 39, the phase difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24 can be arbitrarily set.
The speed change mechanism 38 has a constant speed / double speed switching function of the second eccentric drive shaft 24 with respect to the first eccentric drive shaft 22.
Further, the forward / reverse switching mechanism 37 is a gear type or belt type transmission mechanism and has a function of forward / reverse switching.

With the configuration described above, the phase difference, rotation direction, and rotation speed difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24 can be freely adjusted.
Therefore, in this embodiment, the variable mechanism of the drive device 30 corresponds to the speed change mechanism 38, the forward / reverse switching mechanism 37, and the third clutch 39. The drive device 30 having this configuration has a feature that the versatility and the reliability are very high.

  FIG. 13 is a diagram showing a second embodiment of the drive device 30. As shown in FIG. In this figure, the drive device 30 rotates the first eccentric drive shaft 22 for rotating the first eccentric drive shaft 24, the first motor 32A, the first flywheel 34A, the first clutch & brake 36A, and the second eccentric drive shaft 24. A second motor 32B, a second flywheel 34B, a second clutch & brake 36B for driving, and a synchronization control system 40 for controlling the synchronization of the first motor 32A and the second motor 32B are provided.

  The first motor 32A, the first flywheel 34A, and the first clutch & brake 36A rotate the first eccentric drive shaft 22. The second motor 32B, the second flywheel 34B, and the second clutch & brake 36B rotate the second eccentric drive shaft 24. The first motor 32A and the second motor 32B are configured to be capable of switching the rotation direction to the same direction or the reverse direction.

  Furthermore, the synchronous control system 40 controls the first motor 32A and the second motor 32B, and can arbitrarily set the phase difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24. On the other hand, the speed of the second eccentric drive shaft 24 can be switched between constant speed and double speed.

With the configuration described above, the phase difference, rotation direction, and rotation speed difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24 can be freely adjusted.
Therefore, in this embodiment, the variable mechanism of the drive device 30 corresponds to the first motor 32A and the second motor 32B and the synchronous control system 40. The drive device 30 having this configuration is characterized in that two axes are electrically synchronized.
Compared to FIG. 12, there is a cost reduction effect due to element reduction, and motion switching (phase adjustment) can be further speeded up.

  FIG. 14 is a diagram of a third embodiment of the drive device 30. In this figure, the drive device 30 is driven by a first motor 32A, a first flywheel 34A, a first clutch & brake 36A, and a first flywheel 34A for driving the first eccentric drive shaft 22 to rotate. A transmission mechanism 42, a forward / reverse switching mechanism 43, and a second clutch & brake 36B for rotationally driving the eccentric drive shaft 24 are provided.

The first motor 32A, the first flywheel 34A, and the first clutch & brake 36A rotate the first eccentric drive shaft 22.
The transmission mechanism 42 has a constant speed / double speed switching function of the second eccentric drive shaft 24 with respect to the first eccentric drive shaft 22.
Further, the forward / reverse switching mechanism 43 is a gear-type or belt-type transmission mechanism and has a function of forward / reverse switching.

  The second clutch & brake 36B can arbitrarily set the phase difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24, and rotationally drives the second eccentric drive shaft 24.

With the configuration described above, the phase difference, rotation direction, and rotation speed difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24 can be freely adjusted.
Therefore, in this embodiment, the variable mechanism of the drive device 30 corresponds to the speed change mechanism 42, the forward / reverse switching mechanism 43, and the second clutch & brake 36B. The drive device 30 having this configuration is characterized in that the motor and the flyhole can be omitted in one unit.

  FIG. 15 is a diagram of a fourth embodiment of the drive device 30. In this figure, the drive device 30 rotates the first eccentric drive shaft 22 for rotating the first eccentric drive shaft 24, the first motor 32A, the first flywheel 34A, the first clutch & brake 36A, and the second eccentric drive shaft 24. A servo motor 44 for driving, and a synchronization control system 40 for controlling the synchronization of the first motor 32A and the servo motor 44 are provided.

The first motor 32A, the first flywheel 34A, and the first clutch & brake 36A rotate the first eccentric drive shaft 22. The servo motor 44 drives the second eccentric drive shaft 24 to rotate.
The servo motor 44 can switch the rotation direction to the same direction or the reverse direction with respect to the first motor 32A, and the speed of the second eccentric drive shaft 24 with respect to the first eccentric drive shaft 22 is made constant speed and double speed. It can be switched to.

  Furthermore, the synchronous control system 40 can control the first motor 32A and the servo motor 44 to arbitrarily set the phase difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24.

With the configuration described above, the phase difference, rotation direction, and rotation speed difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24 can be freely adjusted.
Therefore, in this embodiment, the variable mechanism of the drive device 30 corresponds to the servo motor 44 and the synchronous control system 40. The drive device 30 having this configuration is characterized in that the flywheel is eliminated from the second eccentric drive shaft 24 with a light load.

Using the above-described apparatus, the method of the present invention adjusts the phase difference, rotation direction, and rotation speed difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24.
That is, as illustrated in the first to fifth slide motions described above, the phase difference between the first eccentric drive shaft 22 and the second eccentric drive shaft 24 is set, and the second eccentricity with respect to the first eccentric drive shaft 22 is set. The speed of the drive shaft 24 is switched to constant speed or double speed, and the rotation direction is switched to the same direction or the reverse direction.

With the apparatus and method of the present invention described above, productivity can be maximized by changing the slide motion for each mold.
Further, since the speed of the first eccentric drive shaft 22 and the second eccentric drive shaft 24 during the press cycle is constant, it can be driven by a flywheel. Therefore, a high-cost servo motor is unnecessary, and a compact motor can be made compact and low in cost.

  In addition, the three links (first link 12, second link 14, and third link 16) constituting the device of the present invention are links with only two nodes (two-node links), and can be easily manufactured. There is no bending force on the link.

  In addition, this invention is not limited to embodiment mentioned above, Of course, it can change variously in the range which does not deviate from the summary of this invention.

1 is an overall configuration diagram of a variable motion link press according to the present invention. It is a schematic diagram which shows the 1st slide motion of the variable motion link press 10 by this invention. It is an operation diagram of the 1st slide motion (standard motion). It is a schematic diagram which shows the 2nd slide motion of the variable motion link press 10 by this invention. It is an operation diagram of the 2nd slide motion (deep drawing motion). It is a schematic diagram which shows the 3rd slide motion of the variable motion link press 10 by this invention. It is an operation | movement diagram of a 3rd slide motion (deep drawing + quick return motion). It is a schematic diagram which shows the 4th slide motion of the variable motion link press 10 by this invention. It is an operation diagram of the 4th slide motion (low-speed touch motion). It is a schematic diagram which shows the 5th slide motion of the variable motion link press 10 by this invention. It is an operation diagram of the 5th slide motion (1 motor stop motion). 1 is a diagram illustrating a first embodiment of a drive device 30. FIG. FIG. 3 is a diagram showing a second embodiment of a drive device 30. FIG. 4 is a diagram of a third embodiment of a drive device 30. FIG. 6 is a diagram of a fourth embodiment of a drive device 30. It is a schematic diagram of the quick return mechanism of the link press of patent document 1. FIG. 10 is a schematic diagram of a slide drive mechanism of a servo press of Patent Document 2. FIG.

Explanation of symbols

1 slide, 10 variable motion link press,
12 First link, 13 First node,
14 second link, 15 second node,
16 3rd link, 17 3rd node, 18 4th node,
22 first eccentric drive shaft, 24 second eccentric drive shaft,
30 drive device, 32A first motor, 32B second motor,
34A first flywheel, 34B second flywheel,
36A 1st clutch & brake, 36B 2nd clutch & brake,
37 Forward / reverse switching mechanism, 38 transmission mechanism, 39 third clutch 40 synchronization control system, 42 transmission mechanism,
43 Forward / reverse switching mechanism, 44 Servo motor

Claims (6)

A first link that is attached to the lower surface of the upper die and is vertically attached to a slide that moves up and down;
A second link having a lower end rotatably attached to the upper end of the first link at a second node and extending upward;
A third link with a lower end rotatably attached to the upper end of the first link at the second node and extending obliquely upward;
A first eccentric drive shaft that is located vertically above the first node and that eccentrically moves the third node at the upper end of the second link with a constant first eccentric amount;
A second eccentric drive shaft that eccentrically moves the fourth node of the upper end portion of the third link with a constant second eccentric amount;
A drive device that rotationally drives the first eccentric drive shaft and the second eccentric drive shaft;
The drive, possess the first eccentric drive shaft and the phase difference of the second eccentric drive shaft, the direction of rotation, a variable mechanism capable of adjusting the rotational speed difference,
The variable mechanism can arbitrarily set a phase difference between the first eccentric drive shaft and the second eccentric drive shaft, and the speed of the second eccentric drive shaft is switched between constant speed and double speed with respect to the first eccentric drive shaft. A variable motion link press characterized by being capable of switching the direction of rotation in the same direction or in the opposite direction . The drive device includes: a first motor, a first flywheel, and a first clutch and brake for driving the first eccentric drive shaft to rotate;
A second motor, a second flywheel, and a second clutch and brake for rotationally driving the second eccentric drive shaft;
The variable motion link press according to claim 1, further comprising a speed change mechanism, a forward / reverse switching mechanism, and a third clutch that connect between the first eccentric drive shaft and the second eccentric drive shaft. The drive device includes: a first motor, a first flywheel, and a first clutch and brake for driving the first eccentric drive shaft to rotate;
A second motor, a second flywheel, and a second clutch and brake for rotationally driving the second eccentric drive shaft;
The variable motion link press according to claim 1, further comprising a synchronization control system that controls synchronization of the first motor and the second motor. The drive device includes: a first motor, a first flywheel, and a first clutch and brake for driving the first eccentric drive shaft to rotate;
The variable motion link press according to claim 1, further comprising: a speed change mechanism, a forward / reverse switching mechanism, and a second clutch and brake for rotationally driving the second eccentric drive shaft by the first flywheel. The drive device includes: a first motor, a first flywheel, and a first clutch and brake for driving the first eccentric drive shaft to rotate;
A servo motor for rotationally driving the second eccentric drive shaft;
The variable motion link press according to claim 1, further comprising a synchronization control system that controls synchronization between the first motor and the servo motor. A first link that is attached to the lower surface of the upper die and is vertically attached to a slide that moves up and down;
A second link having a lower end rotatably attached to the upper end of the first link at a second node and extending upward;
A third link with a lower end rotatably attached to the upper end of the first link at the second node and extending obliquely upward;
A first eccentric drive shaft that is located vertically above the first node and that eccentrically moves the third node at the upper end of the second link with a constant first eccentric amount;
A second eccentric drive shaft that eccentrically moves the fourth node of the upper end portion of the third link with a constant second eccentric amount;
A drive device that rotationally drives the first eccentric drive shaft and the second eccentric drive shaft;
The phase difference between the first eccentric drive shaft and the second eccentric drive shaft is set, the speed of the second eccentric drive shaft is switched to the constant speed or double speed with respect to the first eccentric drive shaft, and the rotation direction is the same direction. Alternatively, the motion switching method of the variable motion link press is characterized by switching in the reverse direction .

Images