JPH06190598A - Drive force transmission device for mechanical press - Google Patents

Abstract

(57) [Summary] [Purpose] The operation speed of slides, etc. can be controlled arbitrarily, and it is possible to handle press work of various types. [Structure] The power transmission shaft 4 for transmitting the rotational energy of the flywheel 2 is a first split shaft 4 on the flywheel 2 side.
a and the second split shaft 4b on the power take-out gear 5 side.
The planetary gear device 19 is assembled between the split shafts 4a and 4b.
The planetary gear unit 19 can be driven by the servo motor 18. The power take-out gear 5 is attached to the output part of the planetary gear unit. Power is transmitted from the power take-off gear 5 to each drive mechanism. The rotation of the output portion of the planetary gear unit 19 is controlled by the servo motor 18, and the rotation of the power take-out gear 5 is changed.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive force transmission device for transmitting a drive force of a main motor to a slide drive mechanism, a work transfer drive mechanism and the like in a mechanical press.

[0002]

2. Description of the Related Art In a mechanical press, a slide holding mechanism applies a pressing operation to a slide that holds a die, and a work conveying drive mechanism is also operated in a timing synchronized with this pressing operation to continuously form a work. Some are designed to be processed.

An example of the driving force transmission device for transmitting the driving force to the slide driving mechanism and the work transfer driving mechanism is shown in FIG.
As shown in. That is, the flywheel 2 is rotated by driving the main motor 1 and the flywheel 2 is rotated.
When rotational energy is stored in the flywheel 2
By inserting a clutch 3 that can be turned on and off, the rotational energy stored in the flywheel 2 is transmitted to the power transmission shaft 4 as a driving force, and the driving force is taken out from the power transmission shaft 4. The drive force extracted by the power take-out gear 5 is transmitted to the pinion 7 coaxial with the relay gear 6 via the relay gear 6, and the slide drive mechanism 8 is rotated by the rotation of the pinion 7. The slide 9 holding the die is driven to be pressed, and the rotation of the relay gear 6 is simultaneously taken out by the bevel gear mechanism 10 or the like and transmitted to the work transfer drive mechanism 12. Reference numeral 11 represents a brake of the power transmission shaft 4.

[0004]

However, in the case of the above-mentioned conventional driving force transmission mechanism, the movements of the slide driving mechanism 8 and the work transfer driving mechanism 12 are structurally different from each other in terms of attachment / detachment of the clutch 3.
Since it can be controlled only by changing the speed of the flywheel 2, for example, the operation speed of the slide 9 can be arbitrarily controlled during the stroke, or press working can be performed with the slide 9 temporarily stopped at the bottom dead center. I couldn't make it happen. Therefore, there has been a limit to the press forming work for many kinds of materials.

Further, in the case of the above-mentioned conventional driving force transmission mechanism,
To operate the slide drive mechanism 8 in the stopped state,
Since the clutch 3 is put in the rotating flywheel 2, there is a problem that a mechanical shock is generated and a large noise is generated at that time, and the clutch 3 has a frictional structure. Since connecting pads such as inserts are consumable items, it is necessary to prepare a large number of pads and periodically check and replace them.

In view of this, the present invention makes it possible to arbitrarily control the operating speed of the slide or the like so as to cope with press forming work for a wide variety of materials, and also to generate mechanical shock or replace parts. Therefore, it is possible to realize maintenance-free by eliminating the use of a clutch that needs to be performed and to reduce the cost.

[0007]

In order to solve the above problems, the present invention takes out the rotational energy stored in a flywheel by driving a main motor from a power transmission shaft by a power take-out gear and transmits it to a drive mechanism. In the driving force transmission device for a mechanical press, the power transmission shaft is divided into a first split shaft on the flywheel side and a second split shaft on the power takeoff gear side, and a servomotor is provided between the split shafts. A driven planetary gear device is assembled, and the power take-out gear is attached to an output part of the planetary gear device.

Further, a planetary gear device is assembled between the respective split shafts, and a variable torque brake is provided in a part of the planetary gear device. Further, a control device for controlling the variable torque brake is provided. And

Further, a planetary gear device which is driven by a servomotor is assembled between the split shafts, and a power take-out gear and a brake are provided at an output portion of the planetary gear device, and the flywheel and the first wheel are provided. It is preferable that a detaching mechanism is provided between the split shaft and a gear coupling is used as the detaching mechanism.

Furthermore, a differential device for returning a part of the output of the planetary gear device to the input side may be provided, and a servo motor may be connected to the differential device.

[0011]

When the planetary gear device is assembled to the split portion of the power transmission shaft, the rotational energy of the flywheel is transmitted from the first split shaft to the planetary gear device and taken out by the power take-off gear. When the rotation of a part of the planetary gear device is controlled, the rotation speed of the power take-out gear can be changed, so that the operating speed of the drive mechanism can be arbitrarily controlled. Therefore, it becomes possible to arbitrarily control the operation speed of the slide or the like during one stroke.

Further, when a variable torque brake is installed in a part of the planetary gear device instead of the servomotor, if the rotational speed of a part of the planetary gear device is controlled by the variable torque brake, the rotation of the power take-out gear is rotated. Since the speed can be changed, the operating speed of the drive mechanism can be arbitrarily controlled.

Further, when the output portion of the planetary gear device driven by the servo motor is equipped with a power take-out gear and a brake, the rotation speed of the servo motor is changed with the brake applied and the drive mechanism stopped. When set to the calculated value, the rotational speed of the first split shaft can be made equal to the rotational speed of the flywheel. Therefore, between the flywheel and the power transmission shaft, it is possible to use an attachment / detachment mechanism that does not require a connection pad such as a gear coupling. Further, when the rotation of the output portion of the planetary gear device is controlled by the servo motor, the rotation speed of the power take-out gear can be changed, so that the operating speed of the drive mechanism can be arbitrarily controlled.

Furthermore, if a differential device is provided for returning a part of the output of the planetary gear device to the input side and the servo motor is connected to this differential device, the braking force of the servo motor is minimized. Can be

[0015]

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

FIG. 1 shows a first embodiment of the present invention.
The case where the rotational energy of the flywheel is transmitted to the slide as a driving force will be described. That is, in the drive force transmission device of the mechanical press having the same configuration as shown in FIG. 15, the power transmission shaft 4 that receives the rotational energy of the flywheel 2 via the clutch 3 is connected to the flywheel 2 and the power take-out gear 5. A planetary gear composed of a sun gear 15, a planetary gear 13, and an internal gear ring gear 14 which are successively meshed between the split shafts 4a and 4b by splitting at a position between them to form a first split shaft 4a and a second split shaft 4b. A device 19 is arranged to connect the first split shaft 4a on the flywheel 2 side to the sun gear 15, and connect the second split shaft 4b to the planet carrier 20 of the planet gear 13 as a power take-off shaft. The power take-off gear 5 is attached to the second split shaft 4b, and the rotational energy of the flywheel 2 is transmitted from the first split shaft 4a to the power take-off gear 5 via the planetary gear unit 19. The power take-off gear 5 takes out the power to be applied to the slide drive mechanism 8. Further, an outer tooth ring gear 16 is fixedly provided on the outer peripheral portion of the inner tooth ring gear 14, and the pinion is meshed with the outer tooth ring gear 16. 17, AC
Attach to the axis of a servo motor 18, such as a servo motor,
The servomotor 18 is driven to control the rotation of the planet carrier 20 of the planet gear 13 which is the output part of the planetary gear device 19, and the power take-off gear 5 on the second split shaft 4b with respect to the first split shaft 4a which is the input part. The rotation speed of the slide 9 can be changed so that the operation speed of the slide 9 which is moved up and down by the slide drive mechanism 8 can be arbitrarily controlled. In FIG. 1, the same parts as those in FIG. 15 are designated by the same reference numerals.

When the clutch 3 is put into the flywheel 2 which is rotated by the drive of the main motor 1, the rotational energy of the flywheel 2 is taken out to the first split shaft 4a via the clutch 3 and the planet The power transmitted to the second split shaft 4b via the gear device 19 and applied to the slide drive mechanism 8 is taken out from the power take-out gear 5 on the second split shaft 4b. At this time, the planetary gear device 1
Since the rotation speed of the planet carrier 20 of the planet gear 13 that serves as the output unit of 9 can be controlled by the servo motor 18, the rotation speed of the power take-out gear 5 can be arbitrarily changed. Therefore, the operation of the slide 9 moved up and down by the slide drive mechanism 8 can be arbitrarily controlled.

More specifically, the rotation speed of the first split shaft 4a is Ns, the rotation speed of the second split shaft 4b is Np, and the rotation speed of the internal gear ring gear 14 of the planetary gear unit 19 driven by the servomotor 18. Is Nd, and the number of teeth of the sun gear 15, the planetary gear 13, and the internal gear ring gear 14 is Z1, respectively.
Z2 and Z3 can be expressed as Nd = Np- (Z1 / Z3) .times. (Ns-Np) ... Z2 = (Z3-Z1) / 2 ....

Therefore, during normal operation, Np = Ns,
Since Ns = Ns, the servomotor 18 may control the rotational speed of the internal gear ring gear 14 so that Nd = Ns from the above equation.

On the other hand, when the servo motor 18 is stopped,
Since Nd = 0 and Ns = Ns, from the above equation, Np
= {Z1 / (Z1 + Z3)} * Ns, and power is taken out from the power take-out gear 5 and transmitted to the slide drive mechanism 8 under such conditions.

When the press is stopped, that is, when the operation of the slide 9 is stopped, Np =
Since 0 and Ns = Ns, Nd = (-
Z1 / Z3) × Ns so that the internal gear ring gear 14
The number of revolutions may be controlled by the servo motor 18.

As described above, in the present invention, by controlling the rotation of the planetary gear unit 19 by the servo motor 18, the operating speed of the slide 9 can be arbitrarily controlled during one stroke, and therefore, the aluminum molding can be performed. Although it is sometimes particularly effective, it becomes possible to perform the molding such that the pressed state is maintained for a certain time after the completion of the press molding, and it is possible to cope with the press molding of various kinds of materials.

In FIG. 1, the internal gear ring gear 14
May be meshed with a second planetary gear that is coaxially arranged with the planetary gear 13. In this case, when the number of teeth of the second planetary gear is Z4, Nd = {1+ (Z1.Z4 / Z3.Z2 )} × Np−
It can be expressed as (Z1.Z4 / Z3.Z2) .times.Ns.

Next, FIG. 2 shows a second embodiment of the present invention. In the same construction as shown in FIG. 1, the power take-off gear 5 is provided on the outer peripheral portion of the internal gear ring gear 14 of the planetary gear unit 19.
Is fixed and the internal gear ring gear 14 is used as an output part,
The brake 11 is connected to the carrier 21 of the internal gear ring gear 14 via the hollow shaft 22, and the second split shaft 4b connected to the planet carrier 20 of the planet gear 13 is connected to the servo motor 18.
It can be driven by.

In the case of the embodiment of FIG. 2, the rotation speed of the first split shaft 4a is Ns, the rotation speed of the second split shaft 4b driven by the servomotor is Nd, and the rotation of the internal gear ring gear 14 of the planetary gear unit 19 is changed. The number of teeth of the sun gear 15, the planetary gear 13, and the internal gear ring gear 14 is Z1, respectively.
Letting Z2 and Z3, it can be expressed as Nd = Np / {1+ (Z1 / Z3)} + Ns / {1+ (Z3 / Z1)} ....

Therefore, during normal operation, Np = Ns,
Since Ns = Ns, the rotation speed of the planet carrier 20 of the planet gear 13 may be controlled by the servomotor 18 via the second split shaft 4b so that Nd = Ns from the above formula. When the servo motor 18 is stopped,
Since Nd = 0 and Ns = Ns, from the above equation, Np
= (-Z1 / Z3) * Ns, and power is taken out from the power take-out gear 5 under such conditions. Further, when the press is stopped, Np = 0 and Ns = Ns are satisfied. Therefore, from the above equation, Nd = (Z1 / (Z1 + Z3)). Times.Ns is established by the servomotor 18 of the planetary gear 13. The rotation speed of the planet carrier 20 may be controlled.

In FIG. 2, the internal gear ring gear 14
May be engaged with a second planetary gear that is coaxially integrated with the planetary gear 13, or the power take-out gear 5 may be provided on the hollow shaft 22. In this case, if the number of revolutions of the servomotor 18 is Nd, the number of revolutions of the hollow shaft 22 is Np, and the number of teeth of the second planetary gear is Z4, then Nd = Np x1 / {1+ (Z1.Z4 /Z3.Z2 )}
It can be expressed as + Ns × 1 / {1+ (Z2.Z3 /Z1.Z4)}.

Next, FIG. 3 shows a third embodiment of the present invention. In the same construction as shown in FIG. 2, the first split shaft 4a is connected to the carrier 21 of the internal gear ring gear 14 and the second The split shaft 4b is connected to the sun gear 15, and the planetary carrier 20 of the planetary gear 13 is provided with the power take-out gear 5 and the brake 11 by means of the hollow shaft 22, and the planetary gear 13 is used as an output portion.

Also in the case of the embodiment shown in FIG. 3, the servo motor 1
By controlling the rotation of the planetary gear unit 19 with 8, the operating speed of the slide 9 can be arbitrarily controlled as in the case of the embodiments of FIGS. 1 and 2.

Incidentally, also in FIG. 3, the internal ring gear 1
4 may be configured to mesh with a second planetary gear that is coaxially and integrally arranged with the planetary gear 13.

FIG. 4 shows a fourth embodiment of the present invention.
In a configuration similar to that shown in FIG. 3, the planetary gear 13 is used as a first planetary gear, a second planetary gear 23 coaxially integrated with the first planetary gear 13 is provided, and the carrier 20 of the planetary gears 13 and 23 is provided as a first planetary gear. The internal toothed ring gear 14 is connected to the split shaft 4a and the second planetary gear 23 is meshed with the internal toothed ring gear 14, and the carrier 21 is attached to the hollow shaft 22.
4 is the output section.

FIG. 5 shows a fifth embodiment of the present invention. In the same construction as that of FIG. 1, the planetary gear 13 is the first planetary gear and the first planetary gear 13 is coaxially and integrally arranged. The two planetary gears 23 are provided, the inner toothed ring gear 14 is meshed with the second planetary gears 23 to connect the carrier 21 to the first split shaft 4a, and the sun gear 15 to the second split shaft 4b.
And the carrier 20 of the planetary gears 13, 23
Is connected to the hollow shaft 22 on the second split shaft 4b, and a pinion 17 driven by a servomotor 18 is meshed with a gear 25 provided on the hollow shaft 22 to form a sun gear 15
Is the output section.

Further, FIG. 6 shows a sixth embodiment of the present invention. In the same construction as in FIG.
As a planetary gear, a second planetary gear 23 coaxially integrated with the first planetary gear 13 is provided, and the second planetary gear 2 is also provided.
3, the internal gear ring gear 14 is meshed with the sun gear 15
Is connected to the second split shaft 4b, and the sun gear 15 is used as an output portion.

In the embodiments shown in FIGS. 4 to 6, the same effects as those of the above embodiments can be obtained.

Next, FIGS. 7 to 12 show modifications of the embodiment shown in FIGS. 1 to 6, respectively. Instead of the planetary gear unit 19 having the internal gear ring gear 14, the second sun gear 24 is replaced with the second sun gear 24. The planetary gear device 19 'is used.

That is, FIG. 7 shows a seventh embodiment in which the embodiment of FIG. 1 is modified. In the same structure as that of FIG. 1, a first split shaft 4a and a second split shaft 4b are provided between the first split shaft 4a and the second split shaft 4b. The first sun gear 15 and the second sun gear 24 and the planetary gear device 19 ′ including the coaxially integrated first planetary gear 13 and second planetary gear 23 meshing with the first sun gear 15 and the second sun gear 24 are arranged to move the first sun gear 15 to the first sun gear 15. The second sun gear 24 is connected to one end of the second split shaft 4b while being connected to the first split shaft 4a, and the planetary gears 13, 2 are connected.
The carrier 20 of No. 3 is connected to the hollow shaft 22 arranged on the second split shaft 4b, the power take-out gear 5 and the brake 11 are provided on the hollow shaft 22, and the servo is provided at the other end of the second split shaft 4b. The motor 18 is connected.

In the above, the rotation speed of the first split shaft 4a is Ns, the rotation speed of the second split shaft 4b by the servomotor 18 is Nd, and the hollow shaft 22 which is the revolution speed of the planetary gears 13 and 23 as the output portion. If the number of revolutions is Np and the numbers of teeth of the first sun gear 15, the first planetary gear 13, the second planetary gear 23, and the second sun gear 24 are Z1, Z2, Z4, and Z5, respectively, then Nd = {1 -(Z1 ・ Z4 / Z2 ・ Z5)} × Np +
It can be expressed as (Z1 .Z4 / Z2 .Z5) .times.Ns. Therefore, the servo motor 1
By controlling the number of rotations of 8, the operation speed of the slide 9 can be arbitrarily controlled.

Next, FIG. 8 is a modification of the embodiment of FIG.
This shows a further developed eighth embodiment, in which the first split shaft 4
a and the second split shaft 4b between the first sun gear 15 and the second
A planetary gear device 1 including a sun gear 24 and coaxial planetary gears 13 and 23 meshing with the sun gears 15 and 24.
9'is arranged and the first sun gear 15 is connected to the first split shaft 4
a and the second sun gear 24 are respectively connected to the second split shaft 4b, and the rotational energy of the flywheel 2 is transmitted from the first split shaft 4a to the power take-off gear 5 via the planetary gear unit 19 '. Power is taken out by the power take-off gear 5 and the hollow shaft 22 is attached to the carrier 20 of the planetary gears 13, 23.
A gear 25 is attached via a pinion 17, and a shaft 26 of the pinion 17 that meshes with the gear 25 is connected to a variable torque brake 28 that is operated based on a command from a control device 27. By controlling the orbital speed of the planetary gears 13, 23 of the planetary gear device 19 ', the rotational speed of the power take-out gear 5 can be changed via the sun gear 24 serving as an output part, and the slide drive mechanism 8 moves up and down. The operation speed of the slide 9 to be operated can be arbitrarily controlled.

The control device 27 includes the shaft 2 of the pinion 17.
Rotary encoder 29 as a speedometer provided on the 6
A brake controller 30 which is adapted to receive a feedback signal from the brake controller 30 and which sends a drive signal to the variable torque brake 28;
Rotary encoder 31 provided as a speedometer on 4b,
The press controller 33 is configured to send an operation signal to the brake controller 30 based on a signal from 32.

In the case of the embodiment shown in FIG. 8, when the clutch 3 is put into the flywheel 2 which is rotated by the drive of the main motor 1, the rotational energy of the flywheel 2 is transmitted through the clutch 3 to the first split shaft. 4a, and the second split shaft 4b via the planetary gear unit 19 '.
Is transmitted to the slide drive mechanism 8,
It is taken out from the power take-out gear 5 on the split shaft 4b. At this time, since the revolution numbers of the planetary gears 13 and 23 of the planetary gear device 19 'can be controlled by the variable torque brake 28, the rotational speed of the power take-out gear 5 is controlled. Can be changed arbitrarily. Therefore, the operation of the slide 9 moved up and down by the slide drive mechanism 8 can be arbitrarily controlled during one stroke. In this case, a command is sent from the press controller 33 to the brake controller 30 based on the number of rotations of the first split shaft 4a detected by the rotary encoder 31, and the variable torque brake 28 is operated by the command of the brake controller 30, so that the planetary gears are operated. Device 1
The revolution speed of the 9'-planetary gears 13, 23 is controlled to change the rotational speed of the power take-out gear 5 via the sun gear 24 serving as an output part. At this time, the rotation speed of the pinion 17 detected by the rotary encoder 29 is fed back to the brake controller 30, and the rotation speed of the power take-out gear 5 detected by the rotary encoder 32 is fed back to the press controller 33.

The above operation will be described in detail. Now, the first split shaft 4
The rotation speed of a is Ns, the rotation speed of the second split shaft 4b is Np, the revolution speed of the planet gears 13 and 23 (= rotation speed of the hollow shaft 22) is Nd, and the first sun gear 15 and the first planetary gears are also used. Gear 13,
Letting the numbers of teeth of the second planetary gear 23 and the second sun gear 24 be Z1, Z2, Z4 and Z5 respectively, Nd = Np x1 / {1- (Z1.Z4 / Z2 .Z5)}
+ Ns × 1 / {1- (Z2 .Z5 / Z1 .Z4)} can be expressed.

Therefore, during normal operation, from the above equation,
If the revolution numbers of the planetary gears 13 and 23 are controlled by the variable torque brake 28 so that Nd = Ns, then Np =
Ns.

On the other hand, when the variable torque brake 28 is fully operated, Nd = 0, so Np =
Ns × (Z1 · Z4 / Z2 · Z5), and power is taken out from the power take-out gear 5 and transmitted to the slide drive mechanism 8 under these conditions.

When stopping the press, that is,
When stopping the operation of the slide 9, from the above equation,
If the revolutions of the planetary gears 13 and 23 are controlled by the variable torque brake 28 so that Nd = Ns.times.1 / {1-Z2.Z5 / Z1.Z4}, then Np = 0.

As described above, in the embodiment of FIG. 8, the operating speed of the slide 9 can be arbitrarily controlled during one stroke by controlling the rotation speed of the planetary gear device 19 'by the variable torque brake 28. Therefore, it is possible to perform molding that holds the pressed state for a certain period of time after the completion of press molding, which is particularly effective during aluminum molding, or return to the standby position at high speed after molding. It is also possible to deal with press molding of various kinds of materials and it is also advantageous in improving efficiency.

In the embodiment of FIG. 8, the servo motor 18 may be used instead of the variable torque motor 28.

Next, FIG. 9 shows a ninth embodiment in which the embodiment of FIG. 3 is modified. In the same construction as that of the embodiment of FIG. 7, the first sun gear 15 and the second sun gear 24 are The arrangement is reversed, and the arrangements of the first planetary gear 13 and the second planetary gear 23 are reversed. That is, the first planetary gear 1
The first sun gear 15 meshing with the third planetary gear 23 is connected to the second split shaft 4b, and the second sun gear 24 meshing with the second planetary gear 23 is connected to the first split shaft 4a.

In the case of the embodiment shown in FIG. 9, the same effect as that of the embodiment shown in FIG. 7 can be obtained.

FIG. 10 shows a tenth embodiment which is a modification of the embodiment shown in FIG.
In order to transfer the rotational energy of the flywheel 2 to the power transmission shaft 4, the ring gear 34 connected to the side end surface portion of the flywheel 2 and the ring gear 34 are provided between the flywheel 2 and the first split shaft 4a. And a gear 35 fixed to the first split shaft 4a, and an internal tooth ring 36 adapted to be detached between the gears 34, 35 by moving the gears 34, 35 in the axial direction between the outer peripheral portions of the gears 34, 35. A gear coupling 37 is provided so that the rotation of the flywheel 2 is transmitted to the power transmission shaft 4 via the gear coupling 37.

Further, a planetary gear device 19 'is arranged between the first split shaft 4a and the second split shaft 4b, and the planetary gears 13, 23 are arranged.
The carrier 20 is connected to the first split shaft 4a, the first sun gear 15 is connected to one end of the second split shaft 4b, and the power take-out gear 5 is attached to the second sun gear 24 via the hollow shaft 22,
The servo motor 18 is connected to the other end of the second split shaft 4b, and the planetary gear unit 1 is rotated by the rotation of the servo motor 18.
The rotation of the power take-off gear 5 can be controlled via 9 ', and the hollow shaft 22 is further equipped with a brake 11.

Now, with the flywheel 2 and the first split shaft 4a separated by the gear coupling 37, the main motor 1 is driven at a constant rotational speed, while the brake 11
When the servomotor 18 is driven in a state in which the rotation of the second sun gear 24, which serves as the output portion of the planetary gear device 19 ', is stopped by the hollow shaft 22, the planetary gear 1
Since the first and second split shafts 4a are rotated in a state in which the sun gears 3, 23 are revolved around the sun gears 15, 24, the servomotor 18 of the servomotor 18 is controlled so that this rotational speed becomes equal to the rotational speed of the flywheel 2. Control the number of rotations. In this case, since the ring gear 34 and the gear 35 have the same speed, they can be easily connected, and when the brake 11 is released at the time of pre-start and the servo motor 18 is controlled and driven, the first sun gear 15 is rotated. As a result, the rotations of the planetary gears 13 and 23 are controlled, so that the number of rotations transmitted from the second sun gear 24 to the power take-off gear 5 via the hollow shaft 22 can be arbitrarily changed.

In the above, the rotation speed of the first split shaft 4a is Ns, the rotation speed of the second split shaft 4b is Nd, and the planetary gear unit 1 is
The rotation speed of the second sun gear 24, which is the output of 9 ', is Np, and the number of teeth of the first sun gear 15, the first planetary gear 13, the second planetary gear 23, and the second sun gear 24 is Z1. ,
Assuming that Z2, Z4 and Z5, then Nd = (Z2.Z5 / Z1.Z4) * Np-{(Z2.
Z5 / Z1.Z4) -1} Ns.

Therefore, by controlling the Nd, the operation of the slide 9 which is raised and lowered by the slide driving mechanism 8 can be arbitrarily controlled. That is, in preparation for the start of operation, the gear coupling 37 is turned off, the brake 11 is turned on, and the flywheel 2 is rotated while the press is stopped to set the rotational speed to Ns. Next, the servo motor 18 is moved to the above equation Np = 0, Ns =
Rotate at Nd that satisfies Ns. At this time, the press
It is in a stopped state because the brake is applied and the first split shaft 4a is
It rotates at the same speed as s. Since the flywheel 2 and the first split shaft 4a have the same speed, the gear coupling 37 can be connected in this state without causing mechanical shock. With the above, the driving preparation is completed, and at the same time when the brake 11 is released at the time of starting, the Nd of the servomotor 18 is directed toward a predetermined Np and the slide 9 is smoothly started.

As described above, in the embodiment of FIG.
The servo motor 18 drives and stops the slide 9 at the start.
Therefore, the flywheel 2 and the first split shaft 4a can be kept in a connected state at all times, and therefore the flywheel 2 and the power transmission shaft 4 can be connected to each other. It is possible to use the gear coupling 37 that does not require a pad for use.

Further, FIGS. 11 and 12 show the eleventh and twelfth embodiments obtained by modifying the embodiments of FIGS. 5 and 6, respectively. In the embodiment of FIG. 11, the embodiment of FIG. In a similar configuration, the first sun gear 15 is connected to the second split shaft 4b, and the second sun gear 24 is connected to the first split shaft 4a. In the embodiment of FIG. 12, the first sun gear 15 is The second sun gear 24 is connected to the second split shaft 4b, the second sun gear 24 is attached to the hollow shaft 22, and the carrier 2 of the planet gears 13 and 23 is connected.
0 is connected to the first split shaft 4a.

Similar effects can be obtained in the case of the embodiments shown in FIGS.

Here, regarding the above-described first embodiment shown in FIG. 1 to the twelfth embodiment shown in FIG. 12, each gear of the planetary gear device, the axis of the servo motor 18, the axis of the flywheel 2, the power take-out gear 5 are provided. Table 1 shows a combination pattern of connection with the shafts. In Table 1, R
Is the external gear ring gear 14, P is at least one of the planetary gears 13 and 23, S1 is the first sun gear 15, and S2 is the second sun gear 24.

[0058]

[Table 1] By the way, in FIG. 13, in the embodiment shown in FIG. 10, arrows a, b, and e show the flow of electric power when operating.
In addition, the flow of mechanical power is indicated by arrows c and d. More specifically, for example, during low speed press molding,
Most of the energy from the flywheel 2 is not used and is generated and returned to the power system.
The braking force of the servo motor 18 is increased. In this case, assuming that the power of the main motor 1 (arrow a part) is 1 kw, the power of the servo motor 18 (arrow b part) is 0 kw, and the power transmitted from the flywheel 2 to the planetary gear device 19 '(arrow c part) is When the power of the main motor 1 and the power returned to the main motor 1 are added to 77 kw, and the power taken out by the power take-out gear 5 and transmitted to the slide (arrow d part) is 1 kw, the power supply system is generated by the servo motor 18. The power (arrow portion e) returned to is 76 kw, and the servo motor 18 requires a power of 76 kw.
When the bottom dead center of the slide is stopped, the d portion is 0 kw, and the e portion is 77 kw (maximum). Also, during 1/2 reduction press molding, the power distribution is 46.2 kw for the a part, 0 kw for the b part, 77 kw for the c part, 46.2 kw for the d part, and 30.8 kw for the e part, and servo motor 18 A power of 30.8kw is required. Further, when deceleration molding is not performed (when normal molding is performed without acceleration / deceleration), 77 kw for the part a and 15.
The power distribution is 4 kw, 77 kw in the c section, and 92.4 kw, which is the total of the power from the b section and the power in the c section, in the d section.

Looking at each of the above operation modes, the electric power of 76 kw is returned as the maximum value from the servo motor 18 to the power supply system during the low speed press molding. Therefore, the servo motor 18 responds to this maximum value. In order to brake with a large torque, a large size is required.

An embodiment for minimizing the braking force of the servo motor 18 is shown in FIG. That is, instead of electrically returning the energy from the flywheel 2 in FIG. 10, the energy is mechanically returned, and the mechanical power extracted from the output portion of the planetary gear unit 19 'is input to the input portion. So that it can be returned to the first split shaft 4 on the input side of the planetary gear unit 19 '.
In the vicinity of a, the side gear shafts 38, 39 have the first split shaft 4a.
The differential gear 40 is arranged in parallel with the transmission gear 41, the transmission gear 41 is meshed with the power take-out gear 5, and the drive gear 43 is mounted on the same shaft 42 as the transmission gear 41. 43 is engaged with the carriage gear 44 of the differential device 40, and the one side gear shaft 38
The servomotor 18 is connected to the side gear shaft 39, and the pinion 45 is attached to the other side gear shaft 39.
A gear 46 that meshes with is provided in the middle of the first split shaft 4a.

In the case of the embodiment shown in FIG. 14, a part of the mechanical power taken out by the power take-out gear 5 from the output side of the planetary gear unit 19 'is transferred from the transmission gear 41 to the shaft 42, the drive gear 44 and the differential gear. Since it is returned to the planetary gear unit 19 'via the moving device 40, the pinion 45, the gear 46, and the first split shaft 4a,
By selecting the reduction ratio optimally, the servo motor 18
Can have minimal power for speed control.

That is, in the above, at the time of low speed press molding, if the a part and the b part are 0 kw, the c part is 46.2 kw, and the d part is 1 kw, from the power take-off gear 5 to the differential device 40 at the arrow f part. The mechanically returned power of 76kw is the differential 4
0, and the planetary gear device 1 through the arrow g portion.
30.8 kw is mechanically returned to 9 ', and electric power of 45.2 kw is returned from the servo motor 18 through the portion e to the power supply system. Therefore, the total power of the arrow c part and the arrow g part is sent to the planetary gear unit 19 ', and 1 kw at the d part.
The remaining power of 76 kw is mechanically returned to the differential device 40 by using the power of 4 kw, and the power of the servo motor 18 which was required to be 76 kw in FIG. 13 can be covered by 45.2 kw. Further, in the 1/2 reduction press molding, if the a part is 46.2 kw, the b part is 0 kw, the c part is 46.2 kw, and the d part is 46.2 kw, the f part is the differential gear from the planetary gear unit 19 '. Since the power of 30.8 kw mechanically returned to 40 is circulated through the g portion, it becomes 0 kw in the e portion, and the power of the servomotor 18 becomes zero. Further, when the deceleration molding is not performed, 46.2 kw of the part a is transmitted to the part d through the part c, and 46.2 kw of the part b is transferred to the f part in the differential device 40 (in this case, the direction is opposite to the above). To become 1
After being distributed to 5.4 kw and 30.8 kw to the g part, they are summed so as to be added to the value of the c part, and 92.4 kw is obtained in the d part. Therefore, the e section becomes 0 kW.

From the above, in consideration of all operation modes, the maximum power of 77 kW was required in the example of FIG.
In the embodiment of FIG. 14, the maximum power needs to be 46.2 kW, and the servo motor 18 may have a capacity of 60%.

Incidentally, in the embodiment shown in FIG.
The carriage gear 44 as an input portion, the side gear shaft 39 as an output portion, and the side gear shaft 38 as a servo motor connecting portion.
However, these relationships can be arbitrarily selected.

The present invention is not limited to the above embodiment, and for example, the gear coupling 37 shown in the embodiment of FIG. 10 can be similarly adopted in other embodiments. In the above embodiment, only the case of controlling the slide drive mechanism 8 has been described, but at the same time, the power transmission to the work transfer drive mechanism 12 (see FIG. 15) is performed by the output result of this device or similarly controlled. Needless to say, various modifications can be made without departing from the scope of the present invention.

[0066]

As described above, according to the driving force transmission device for a mechanical press of the present invention, a planetary structure in which a servo motor is driven by a split portion of a power transmission shaft for transmitting rotational energy of a flywheel. Assemble the gear device,
In addition, since the power take-out gear for giving power to the drive mechanism is attached to the output part of the planetary gear device, the rotation of the output part of the planetary gear device can be arbitrarily controlled by the servomotor, whereby the power take-out gear can be controlled. The number of rotations can be changed, and, for example, when the slide is operated via a slide drive mechanism, the operation speed of the slide can be arbitrarily controlled during one stroke, and therefore, the slide which is advantageous for aluminum molding can be obtained. It is possible to give a holding operation etc. of the stopped state at the bottom dead center, it is possible to achieve multiple functions corresponding to various kinds of materials, and the divided portion of the power transmission shaft is equipped with a variable torque brake. By installing the planetary gear device, the rotation of the output part of the planetary gear device can be arbitrarily controlled by the variable torque brake, With this, the rotation speed of the power take-out gear can be changed, the operation speed of the slide can be controlled in the same manner as above, and further, the divided portion of the power transmission shaft is driven by the servo motor. In the configuration in which the planetary gear is assembled, by providing a power take-out gear and a brake for transmitting power to the drive mechanism to the output part of the planetary gear, the rotation of the output part of the planetary gear device can be arbitrarily controlled by the servomotor. Since the rotation of the output part can be stopped by the brake together with this, a detachment mechanism that does not require consumables such as a gear coupling can be used as a connection state between the flywheel and the power transmission shaft in advance. Not only does it not cause mechanical shock during transmission, but it also requires maintenance-free operation without replacement of parts. By providing a differential device that returns a part of the output of the planetary gear device to the input side, and connecting a servomotor to this differential device, In addition, the braking force of the servo motor can be minimized, and the servo motor can be downsized.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram showing a first embodiment of a driving force transmission device for a mechanical press of the present invention.

FIG. 2 is a schematic configuration diagram showing a second embodiment of the present invention.

FIG. 3 is a schematic configuration diagram showing a third embodiment of the present invention.

FIG. 4 is a schematic configuration diagram showing a fourth embodiment of the present invention.

FIG. 5 is a schematic configuration diagram showing a fifth embodiment of the present invention.

FIG. 6 is a schematic configuration diagram showing a sixth embodiment of the present invention.

FIG. 7 is a schematic configuration diagram showing a seventh embodiment of the present invention.

FIG. 8 is a schematic configuration diagram showing an eighth embodiment of the present invention.

FIG. 9 is a schematic configuration diagram showing a ninth embodiment of the present invention.

FIG. 10 is a schematic configuration diagram showing a tenth embodiment of the present invention.

FIG. 11 is a schematic configuration diagram showing an eleventh embodiment of the present invention.

FIG. 12 is a schematic configuration diagram showing a twelfth embodiment of the present invention.

FIG. 13 is a schematic diagram showing the flow of electrical power and mechanical power in the tenth embodiment.

FIG. 14 is a schematic configuration diagram showing a thirteenth embodiment of the present invention.

FIG. 15 is a schematic view showing an example of a driving force transmission device of a conventional mechanical press.

[Explanation of symbols]

 1 Main Motor 2 Flywheel 4 Power Transmission Shaft 4a First Split Shaft 4b Second Split Shaft 5 Power Extraction Gear 8 Slide Drive Mechanism (Drive Mechanism) 11 Brake 12 Work Transfer Drive Mechanism (Drive Mechanism) 13 First Planetary Gear (Output 14) Internal toothed ring gear (output) 15 First sun gear (output) 18 Servo motor 19, 19 'Planetary gear device 23 Second planetary gear (output) 24 Second sun gear (output) 27 Control device 28 Variable Torque Brake 30 Brake Controller 31 Rotary Encoder (Speedometer) 33 Press Controller 37 Gear Coupling (Detachment Mechanism) 40 Differential Device

Claims (6)

[Claims] 1. A drive force transmission device for a mechanical press, wherein rotational energy stored in a flywheel by driving a main motor is taken out from a power transmission shaft by a power take-out gear and transmitted to a drive mechanism. Is divided into a first split shaft on the flywheel side and a second split shaft on the power take-off gear side, and a planetary gear device that is driven by a servomotor is mounted between the split shafts, and the planetary gear is A driving force transmission device for a mechanical press, wherein the power take-out gear is attached to an output part of the device. 2. A driving force transmission device for a mechanical press, wherein rotational energy stored in a flywheel by driving a main motor is taken out from a power transmission shaft by a power take-out gear and transmitted to a drive mechanism. Is divided into a first split shaft on the flywheel side and a second split shaft on the power take-off gear side, a planetary gear device is assembled between the split shafts, and a variable torque brake is provided as part of the planetary gear device. A driving force transmission device for a mechanical press, which is characterized in that: 3. A brake controller for sending a drive signal to a variable torque brake, a speedometer provided on the first split shaft,
The driving force transmission device for a mechanical press according to claim 2, further comprising a control device having a press controller that sends an operation signal to the brake controller based on a signal from the speedometer. 4. A drive force transmission device for a mechanical press, wherein the rotational energy stored in a flywheel by driving a main motor is taken out from a power transmission shaft by a power take-out gear and transmitted to a drive mechanism. Is divided into a first split shaft on the flywheel side and a second split shaft on the power take-off gear side, and a planetary gear device that is driven by a servomotor is mounted between the split shafts, and the planetary gear is A drive force transmission device for a mechanical press, characterized in that the power take-out gear is attached to the output part of the device, a brake is equipped, and an attachment / detachment mechanism is provided between the flywheel and the first split shaft. . 5. The driving force transmission device for a mechanical press according to claim 4, wherein a gear coupling is used as the attachment / detachment mechanism. 6. A driving force transmission device for a mechanical press, wherein rotational energy stored in a flywheel by driving a main motor is taken out from a power transmission shaft by a power take-out gear and transmitted to a drive mechanism. Is divided into a first split shaft on the flywheel side and a second split shaft on the power take-off gear side, a planetary gear device is assembled between the split shafts, and the power take-off gear is attached to the output part of the planetary gear device. A differential device is provided for returning a part of the output that is attached and taken out by the power take-out gear to the input side of the planetary gear device, and further, a servo motor is connected to a part of the differential device. A drive force transmission device for a mechanical press, which is characterized in that