JP2001347400A - Press - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a press which can reduce the inertia of a power transmission mechanism using a variable gear, and is ready for the high-load machining from the high-speed machining. SOLUTION: The power transmission mechanism 12 for converting the rotation of a servo motor 11 and transmitting the rotation to a converting means 13 for converting the rotation into the linear motion integrally comprises a planetary gear device capable of achieving the change-over at the transmission ratio of >=2 and a selecting means 59 for selecting the transmission ratio, and the ram operation is controlled by the transmission ratio selected by the selecting means 59 according to the kind of a plate to be pressed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a press device such as a punch press machine, and more particularly to a device using a planetary gear device for a power transmission mechanism.

[0002]

2. Description of the Related Art In a punch press machine, control is performed such that the speed at which a punch tool actually punches a work is reduced during one stroke, and the stroke speed is increased at other times. As a punch press machine capable of such control, a mechanical punch press that changes the speed in one stroke by using a servomotor capable of freely controlling the number of rotations has been proposed.

In some mechanical punch presses, a servomotor drives, for example, a toggle mechanism via a speed reducer to convert rotation into reciprocating motion. The rotation speed of the servomotor is reduced to, for example, approximately 1/10 rotation speed via a speed reducer. In addition, by using a servomotor with a large output and a wide range of rotation speed, not only speed control during the stroke, but also high-speed machining of many holes to machining of large-diameter holes with large loads. This can be realized by controlling the rotation speed of the servo motor.

[0004] However, the above-described servo motor having a large output and a wide variable range of the number of revolutions is a special high-grade motor. In punching, punching is not possible due to shortage of punching tonnage, and high-speed punching cannot be performed if the specification is such that processing with a large load can be performed.

Therefore, the rotational speed of the servomotor is reduced by a speed reducer, a transmission is connected in series with the speed reducer, the rotational speed of the servomotor is reduced to, for example, 1/5 by the speed reducer, and further reduced by the speed reducer. A punch press machine capable of switching to 1/1 or 1/2 has been proposed. During high-speed machining,
By setting to / 1, the overall deceleration rate is reduced to 1/5, and during heavy load machining, the transmission is reduced to 1/2 to reduce the overall deceleration rate to 1/10.

[0006]

However, when a speed reducer and a transmission are connected to the servomotor, a large number of gears built in the speed reducer and the transmission are driven to rotate, and the transmission of the drive to a toggle mechanism or the like is required. There is a problem that the inertia force is increased and the followability of the speed change control in one stroke by the servomotor is deteriorated. Such a problem occurs not only in the punch press but also in various presses that perform speed change control during one stroke.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a press apparatus which can reduce the inertial force of a power transmission mechanism using gears capable of shifting, and can cope with high-speed machining to high-load machining.

[0008]

According to one aspect of the present invention, there is provided a press apparatus, comprising: a drive motor; a power transmission mechanism for converting the number of rotations of the drive motor to transmit; To a linear motion of the ram, wherein the power transmission mechanism comprises two or more planetary gear units,
Selecting means for selecting one of the two or more planetary gear devices, wherein the ram operation is controlled in accordance with the type of plate processing by the transmission ratio selected by the selecting means. According to the first aspect, the rotation speed of the drive motor is converted into an appropriate output and rotation speed by the two or more planetary gear devices, and the output and rotation speed are selected by the selection means provided integrally with the two or more planetary gear devices. Choose the right number of planetary gears. This planetary gear system originally has a small inertial force,
Furthermore, since the selection means for changing the transmission ratio is also integrated,
The power transmission mechanism has a small inertia force as a whole and is small.

According to a second aspect of the present invention, in the first aspect, the planetary gear unit includes a sun gear connected to an input shaft, a planetary gear meshing with the sun gear, and an internal tooth meshing with the planetary gear. An output shaft connected to the planetary gears or the internal gears, wherein the planetary gears are arranged in two or more rows having different transmission ratios, and any one of the sun gear, the planetary gears in the two or more rows, and the internal teeth is arranged in the axial direction. , And any one of the two or more rows of planetary gears is selected and meshed. According to the second aspect, since the planetary gears of the planetary gear device are arranged in two or more rows and any one of them is engaged with the planetary gear device, the inertial force of the planetary gear device for changing the transmission ratio becomes sufficiently small and the planetary gear device becomes compact.

According to a third aspect of the present invention, in the pressing device according to the second aspect, the output shaft is connected to the internal teeth and has a star shape to which a planetary gear is fixed, and the internal teeth are slidable in the axial direction. It is. According to the third aspect, the transmission ratio is changed by a simple mechanism in which the selection means slides the internal teeth.

According to a fourth aspect of the present invention, in the pressing device according to the third aspect, the internal gear has a first speed change position meshing with the first planetary gear train, a second speed change position meshing with the second planetary gear train,
And a lock position that meshes with both the first and second planetary gear trains. According to the fourth aspect, when the lock position is set by the selection means, the operation of the press device can be stopped and fixed.

According to a fifth aspect of the present invention, in the press apparatus according to any one of the first to fourth aspects, the drive motor is a servomotor, and when selecting the transmission ratio of the selecting means, the phase of the switched gear of the planetary gear device is adjusted. Means are provided. According to the fifth aspect, when the transmission ratio of the planetary gear device is changed by the selecting means, the phases of the teeth meshed by the phase matching means are matched, so that the gears can be meshed reliably and easily.

According to a sixth aspect of the present invention, in the first aspect, the selection means selects a transmission ratio at which the ram can output a pressing force required for processing a plate material. According to the sixth aspect, it is possible to cope with high-speed processing or high-load processing according to the type of plate material processing.

According to a seventh aspect of the present invention, there is provided a press apparatus according to the sixth aspect, further comprising a calculating means for calculating a required pressing force from the plate material processing information, wherein the selecting means determines whether or not the calculated pressing force exceeds a predetermined value. The transmission ratio for increasing the pressing force is selected. According to the seventh aspect, the arithmetic means can accurately grasp the type of the plate material processing and perform appropriate processing.

According to an eighth aspect of the present invention, in the pressing apparatus according to the seventh aspect, the selecting means normally selects a transmission ratio in which the pressing force is small, and when the pressing force calculated by the calculating means exceeds a predetermined value, The transmission ratio at which the pressing force is increased is selected. According to the present invention, high-speed processing is usually performed with a small pressing force, and high-load processing is performed by increasing the pressing force only when necessary.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a cross-sectional view of a main part of a side surface of the press device, and FIG. 2 is a device block diagram of a control system of the press device.

First, the structure of the main part of the press device 1 will be described with reference to FIG. The press device 1 has a basic structure for vertically moving the punch die 3 with respect to the press die 2, and converts a servo motor 11 as a drive motor and a rotation speed of the servo motor 11 at a predetermined transmission ratio. Power transmission mechanism 1 for transmission
2 and a conversion means 13 for converting the rotational movement of the power transmission mechanism 12 into a linear movement and moving the ram 4 holding the punch die 3 up and down.

A lower turret 5a for holding a large number of press dies 2 is rotatably attached to a lower frame 10a. An upper turret 5b for holding a large number of punch dies 3 is rotatably attached to the upper frame 10b. A box-shaped frame 14 opening downward is slidably attached to a portal frame 10c erected on the upper frame 10b. Servo motor 11
The power transmission mechanism 12 and the conversion means 13 are integrally attached to a box-shaped frame 14 opened downward.

A serially connected body of the servomotor 11 and the power transmission mechanism 12 is fixed to the side surface 14a of the box-shaped frame 14 with bolts or the like. The conversion means 13 includes a box-shaped frame 14
An eccentric cam mechanism disposed in the eccentric cam 15,
It comprises a crank 17, a slide body 20, and the like. The shafts 15a and 15b at both ends of the eccentric cam 15 are rotatably supported by the box frame 14 via bearings 16. The eccentric cam 15 is rotatably fitted in a hole at the upper end of the crank arm 17 via a bearing (not shown). A connecting bar 19 connected to a lower end of the crank arm 17 by a pin 18 is provided.
The slide body 20 is connected via the. The slide body 20 slides up and down under the guidance of a slide guide 21 fixed in the box-shaped frame 14. A ram switching device 22 is attached to the slide body 20, and the ram 4 is supported by the ram switching device 22 in a selectable manner.

The power transmission mechanism 12 is formed integrally with two or more planetary gear units, and a planetary gear unit 50 that can be switched at a transmission ratio of two or more, and a selection unit 5 that switches the transmission ratio.
9 are integrally formed.

The planetary gear unit 50 includes a casing 51,
An input shaft 52 which is located at the center of the casing 51 and is fitted integrally with the rotation shaft of the servomotor 11, a first sun gear 53 and a second sun gear 54 fitted to the input shaft 52, and the first sun gear Meshing with 53 and the second sun gear 54,
A first planetary gear 55 and a second planetary gear 56 pivotally supported by a shaft protruding from the casing 51; and an axially slidable internal tooth 57 that meshes with either the first planetary gear 55 or the second planetary gear 56; , Projecting from a spline shaft 58a fitted into a spline hole 57a on the inner surface of the internal teeth 57,
An output shaft 58 that is integrally fitted to the shaft 15c of the eccentric cam 15.
And comprising.

The selecting means 59 is a mechanism for slidingly moving the internal teeth 57 to a predetermined position in the axial direction. The selecting means 59 includes a roller 60 fitted in a circumferential groove 57b of the internal teeth 57, and an arm for rotatably supporting the roller 60. A shaft 61 which makes the swingable 62;
It comprises a cylinder 64 connected via an arm 63 for rotating the shaft 61 at a predetermined angle.

The position of the internal teeth 57 in the axial direction by the selecting means 59 is the first speed change position where the first planetary gear 55 and the internal teeth 57 mesh with each other, both the first planetary gear 55 and the second planetary gear 56 and the internal teeth 57 There is a lock position where the gears mesh with each other, and a second shift position where the second planetary gears 56 and the internal teeth 57 mesh with each other.

The first planetary gear 55 and the first sun gear 53 form a first row A of planetary gear trains, and the second planetary gear 56 and the first sun gear 54 form a second row B of planetary gear trains. Has formed. The first row A and the second row B are arranged in parallel with the input shaft 52 at a predetermined interval. When the internal teeth 57 are slid toward the servo motor 11, the first planetary gear 55
And the first gear position where the internal teeth 57 mesh with each other. When the internal teeth 57 are slid toward the side opposite to the servomotor 11, the second
The second shift position is at which the planetary gear 55 meshes with the internal teeth 57. When the speed is reduced to, for example, 1 / a in the first row A and is reduced to, for example, 1 / 2a in the second row B, the first row A for selecting the first row A
In the case of the shift position and the case of the second shift position in which the second row B is selected, a one-to-two speed ratio can be obtained.

Next, the configuration of the control system of the above-described press machine will be described with reference to FIG. In FIG. 2, the control device 33
Is a means for controlling the entire punch press, and includes a computer-type numerical controller 34 and a programmable controller (not shown). The numerical control unit 34 executes the machining program 38 to output an axis feed command to the servomotor 11 for punch driving and motors of the respective axes such as the upper and lower turrets 5a and 5b, and to program a sequence command in the machining program 38. It is means for transferring to the controller unit. The punch drive command output from the numerical controller 34 is input to the servomotor 11 via the servo controller 35. The control device 33 is provided with a parameter setting section 39 for storing various data required for processing other than the processing program 38, and the processing program 38 and the parameter setting section 39 constitute a processing data setting means 37. You.

In the control device 33 having such a basic configuration, a calculating means 36 is provided in this embodiment. The calculation means 36 is means for switching the transmission ratio of the planetary gear device 50 via the selection means 59 in accordance with the type of machining.
Specifically, the switching command s for selecting a predetermined transmission ratio is selected by the selection means 5.
9 is output. Selection means 59 for speed ratio switching operation
Switches the planetary gear train of the planetary gear device 50 to the first row A or the second row B in response to the command s. When switching the selecting means 59, the phase positions of the internal teeth 57 and the phases of the teeth of the sun gears 55 and 56 to be switched are calculated in advance, and the phase matching means 40 for stopping the planetary gear device 50 at the position where the phases match is obtained. Are connected to the numerical controller 34 so as to correspond to the processing type switching control means 36.

The calculating means 36 sets predetermined processing type data, for example, data such as plate thickness, material, tool type, etc., which is a factor greatly affecting the load of punching.
Sheet thickness and material data 3 described in the machining program 38
The punching tonnage or press force required for machining is calculated based on the comparison between the tool type in 8a and the tool command 38b with the predetermined machining type data. When the punching tonnage or the pressing force exceeds a predetermined threshold value, the selection means 59 switches the planetary gear example of the planetary gear device 50 to perform control for switching from high speed to low speed. Therefore, the processing is usually performed at a high speed, and is switched to a low speed when necessary.

Although the thickness and material data 38a are generally described for each machining program 38, a large number of tool commands 38b are described in the machining program 38.
6 causes the above calculation and selection of the transmission ratio to be performed each time the numerical controller 34 reads the tool command 38b.
The plate thickness and material data 38a may be set in the parameter setting unit 39 without being described in the machining program 38. The tool command 38b is a command for selecting the type of the press die 2, and is a command for determining the rotation angles of the turrets 5a and 5b. The type of the press die 2 affects the size of the punched hole, and since the size, particularly the circumference, greatly affects the punch load, it is set as a calculation element by the calculation means 36.

The operation of the press device 1 having the above configuration will be described. In FIG. 1, the rotation of the servomotor 11 is transmitted via a power transmission mechanism 12, and is further converted to vertical movement of the ram 4 via a conversion means 13. When the eccentric cam 15 makes one rotation, the slide body 20 makes one reciprocating movement through the crank 17. In this one reciprocating operation, the punching operation by the punching die 3 is performed once. Since the servo motor 11 is used as a drive source for this punching, it is also possible to perform control to change the vertical speed of the punch die 3 during the stroke.
For example, control can be performed to reduce the speed at which the punching die 3 actually punches a plate material, and to increase the stroke speed at other times. Therefore, high-speed punching can be performed while suppressing noise.

Since the rotation of the servomotor 11 is shifted by the planetary gear device 50 capable of obtaining a large reduction ratio, the pressing force required for the punch can be obtained even if the driving source is a small servomotor 11. In addition, since the planetary gear unit 50 and the planetary gear unit 50 are small and have a small inertial force, the ability of the servo motor 11 to follow the speed change during one stroke is not impaired. Further, since the planetary gear device 50 is small, the servo motor 11 is directly attached to the planetary gear device 50 and the planetary gear device 50 is attached to the eccentric cam 12, so that a space saving structure is obtained.

In the punching, when a small number of small holes or a thin plate material is machined, or when a small punching load is to be machined, the planetary gear train of the planetary gear unit 50 is moved to the first position. In one row A, for example, the transmission ratio is 1 / a
Then, the pressing force is small, but it should be able to handle high speed. Thereby, high-speed punching is performed. This is the normal processing. When processing a thick plate or a large-diameter hole, the row of the planetary gears of the planetary gear unit 50 is set to the second row B, for example, the transmission ratio is set to 1 / 2a. However, a large pressing force
Thus, even if the servo motor 11 has a small output, a large-diameter hole can be punched. As described above, even if the servo motor 11 has a small output, the sun gear train of the planetary gear device 50 is switched by the selecting means 59, so that high-speed and low-load machining and low-speed and large-load machining are performed. And can do both. Servo motor 1
The output characteristic of 1 changes depending on the number of revolutions, and it is difficult to switch between high-speed machining and large-load machining only by controlling the number of revolutions of the servo motor 11. By combining the planetary gear devices 50 that can be switched, efficient control can be performed.

When switching the planetary gear train of the planetary gear device 50, the press device 1 is temporarily stopped. At this time, the phase matching means 40 of FIG. 2 controls the rotation speed of the servomotor 11, and the planetary gear unit 50 is shifted at a position where the internal teeth 57 of FIG. Set to the stop state. Next, the selection means 59 is operated to switch the planetary gear train of the planetary gear device 50.
Thereby, switching of the planetary gear train of the planetary gear device 50 is quickly and reliably performed. When the press apparatus 1 is held in a stopped state, if the internal teeth 57 in FIG. 1 are set at a lock position where they are engaged with both the planetary gears 55 and 56, the press apparatus 1 is in a mechanically locked state. Does not move.

The calculation means 36 performs the above-described calculation for switching the selection means 59 according to the punch load each time the tool command 38b is read out in accordance with the execution of the machining program 38. Output s. Therefore, there is no need for the operator to judge the switching, the operation is easy, and the switching can be realized by the automatic operation. The arithmetic means 36 may output the switching command s in accordance with a predetermined command set in the machining program 38.

FIGS. 3 and 4 show another embodiment of the present invention. These examples are the same as those in FIG. 1 except for the mechanism for switching the planetary gear train. As in the case of FIG. 1, both high-speed and low-load machining and low-speed and large-load machining can be performed, and the inertial force can be reduced.

In FIG. 3, the planetary gear device 70 is rotatably supported by an input shaft 71, a first sun gear 72 and a second sun gear 73 fitted on the input shaft 71, and a holding frame 74. The first planetary gear 75 and the second planetary gear 76 meshing with the first sun gear 72 and the second sun gear 73, the fixed internal teeth 77 meshing with the first planetary gear 75 and the second planetary gear 76, and the holding frame 74. And an output shaft 78 connected via a spline or a key, and a selecting means 79 for moving the holding frame 74 in the axial direction.

The first sun gear 72 and the first planetary gear 75 form a first row A of planetary gear trains, and the second sun gear 73 and the second
The planet gears 76 form a second row B of planetary gear trains. First
The distance between the planetary gear 75 and the second planetary gear 76 is L,
The distance between the first sun gear 72 and the second sun gear 73 is L + α. Therefore, when the holding frame 74 is moved by α in the axial direction, the first row A or the second row B can be selected. Selection means 7
Reference numeral 9 is connected to the holding frame 74 so as to be relatively rotatable, and the holding frame 74 can be slid to a predetermined position in the axial direction by an actuator or the like.

In FIG. 4, the planetary gear device 80 includes an input shaft 81, a first sun gear 82 and a second sun gear 82 fitted on a shaft 81a connected to the input shaft 81 via a spline or a key. 83 and a holding frame 84 rotatably supported by the first sun gear 82 and the second sun gear 83
A first planetary gear 85 and a second planetary gear 86 meshing with
Fixed internal teeth 87 meshing with the first planetary gear 85 and the second planetary gear 86, an output shaft 88 fixed to the holding frame 84,
Selecting means 89 for moving the shaft 81a in the axial direction.

The first sun gear 82 and the first planetary gear 85 form a first row A of planetary gear trains, and the second sun gear 83 and the second
The planetary gears 86 form a second row B of planetary gear trains. First
The distance between the planetary gear 85 and the second planetary gear 86 is L,
The distance between the first sun gear 82 and the second sun gear 83 is L + α. Therefore, if the shaft 81a is moved by α in the axial direction, the first row A or the second row B can be selected. Selection means 89
Is rotatably connected to the shaft 81a, and the shaft 81a can be slid to a predetermined position in the axial direction by an actuator or the like.

The means for converting the rotation of the press device 1 into a linear motion is not limited to the one using the eccentric cam, the crank and the slide body, but may be the one using a toggle mechanism. The press device 1 is not limited to a punch press device, and may be any press device that converts rotation into linear motion and changes the speed during one stroke.

The planetary gear unit 50 of the press device 1
In both cases of 70 and 80, the case where the transmission ratio is two-stage has been described. However, if the planetary gear train is, for example, three or more and the reduction ratio of each column is sequentially changed, the transmission ratio becomes three or more. It becomes possible to make things. Further, the planetary gear units 50, 70, 8
Although the case where the transmission ratio of 0 is deceleration has been described, the transmission ratio may be increased.

[0041]

As described above, according to the press device of the first to eighth aspects, since the planetary gear device is provided with the selection means for changing the transmission ratio while maintaining the inherent low inertia force, In the case where the speed is changed during one stroke, the inertia force can be reduced and the followability to the speed fluctuation can be improved.

According to the pressing device of the second to fifth aspects, the pressing device provided with the planetary gear device can be reduced in size, and the switching performance of the transmission ratio of the pressing force can be improved.

According to the press apparatus of the sixth to eighth aspects, the state at the time of high-speed and low-load processing and the state at the time of low-speed and large-load processing are:
Switching can be automatically performed according to the processing state, and the operation of the operator can be facilitated.

[Brief description of the drawings]

FIG. 1 is a sectional view of a main part of a side surface of a press device.

FIG. 2 is an equipment block diagram of a control system of the press device.

FIG. 3 is another configuration diagram of the planetary gear device of the press device.

FIG. 4 is still another configuration diagram of the planetary gear device of the press device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Press apparatus 11 Servo motor 12 Power transmission mechanism 13 Conversion means 15 Eccentric cam (Conversion means) 33 Control device 36 Processing type correspondence switching control means (Calculation means) 52 Input shaft 50 Planetary gear device 53 First sun gear 54 Second sun Gear 55 First planetary gear 56 Second planetary gear 57 Internal teeth 58 Output shaft 59 Selection means

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI theme coat ゛ (Reference) B30B 1/26 B30B 1/26 C

Claims (8)

[Claims] 1. A drive motor, a power transmission mechanism for converting and transmitting the rotation speed of the drive motor, and a conversion means for converting the transmitted rotation into a linear motion of a ram, wherein the power transmission mechanism comprises: It has two or more planetary gear devices, and selecting means for selecting one of the two or more planetary gear devices,
A press apparatus wherein the ram operation is controlled in accordance with the type of sheet material processing by the transmission ratio selected by the selection means. 2. The two or more planetary gear devices are connected to a sun gear connected to an input shaft, a planet gear meshed with the sun gear, an internal tooth meshed with the planet gear, and connected to the planet gear or the internal gear. The planetary gears are arranged in two or more rows having different transmission ratios, and the sun gear, the two or more rows of planetary gears, and the internal teeth are slidable in the axial direction, and the two rows are provided. The press apparatus according to claim 1, wherein any one of the planetary gears is selected and meshed. 3. The press device according to claim 2, wherein the output shaft is connected to the internal teeth and has a star shape to which a planetary gear is fixed, and the internal teeth are slidable in the axial direction. 4. The internal gear has a first shift position meshing with a first planetary gear train, a second gear shift position meshing with a second planetary gear train, a first planetary gear train and a second planetary gear. 4. The speed ratio switching type planetary gear set according to claim 3, further comprising a lock position meshing with both of the rows. 5. The driving motor is a servo motor,
The press device according to any one of claims 1 to 4, further comprising a phase adjusting unit that adjusts a phase of a gear that can be switched in the planetary gear device when the transmission ratio is selected by the selecting unit. 6. The press apparatus according to claim 1, wherein said selecting means selects a transmission ratio at which said ram can generate a pressing force required for processing a plate material. 7. An arithmetic unit for calculating a necessary press force from plate material processing information, wherein the selecting unit selects a transmission ratio for increasing the press force when the calculated press force exceeds a predetermined value. Item 7. A pressing device according to item 6. 8. The selection means normally selects a transmission ratio at which the pressing force is small, and selects a transmission ratio at which the pressing force increases when the pressing force calculated by the calculation means exceeds a predetermined value. Item 8. The press device according to Item 7.