JP2005305529A - Transfer press - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transfer press having a drive unit, as a base body, in which a slide is made to execute a reciprocating linear motion by a servomotor, and which is commonly used as the drive mechanism of each device, so that high speed operation becomes possible. <P>SOLUTION: In the transfer press, the drive unit working as a base body is provided with the slide members each of which is rotatably connected to the other end of a connecting rod rotatably connected to the eccentric part of an eccentric disc rotated by the servomotor, and is made to perform the reciprocating linear motion. A plurality of punch drive units for driving a punch attached on each slide member are provided side by side in front of the machine table, and a plurality of dies are provided on the bolster facing the punches. The drive unit is used to drive a transfer bar which performs the interprocess transfer of a plurality of fingers capable of grasping workpieces. Furthermore, if necessary, a knockout mechanism is provided side by side coaxially with the punches at the rear of the dies and the drive unit is used to drive the knockout mechanism. The transfer press performs synchronized numerical control of each drive unit and transfers workpieces from an upstream process to a downstream process. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a transfer press in which press processing units corresponding to product processing processes are arranged side by side in a frame, and workpieces processed in an upstream process are sequentially transferred to a downstream process to perform multi-process press processing. is there.

  Patent documents 1 and 2 are known as prior art concerning this invention. The technique described in Patent Document 1 is a punch driving device that reciprocates a punch in correspondence with a plurality of processes arranged in series, a die holder device that mounts a die facing the punch on a bolster, and a coaxial with the die A knockout punch driving device for reciprocating the knockout punch and a transfer driving device for reciprocating a finger capable of gripping the workpiece, and sequentially transferring each workpiece processed in the upstream process to the next downstream process. It is a transfer press that performs press processing, and the punch driving device has a plurality of punch guide mechanisms that can move forward and backward in each process along each movement axis of the punch, and a plurality of punch drives that reciprocate each punch in each process. A linear motor is used to form a unit for each process, and the transfer drive unit moves individually along the transfer axis for transferring workpieces. A plurality of movable finger guide mechanisms and a transfer drive linear motor that reciprocally moves each finger in a single process or in each process group are configured as a single process or in a process group unit. A transfer press configured as a unit for each process with a plurality of sets of knockout punch guide mechanisms that can move forward and backward along each movement axis and a plurality of knockout punch drive linear motors that reciprocate each knockout punch for each process. is there. In addition, the attachment part of the punch guide mechanism or knockout punch guide mechanism includes a plurality of rows of locking grooves provided on the front surface of the frame in the form of long slots parallel to the transfer axis for transferring the workpiece, and the back side of each guide mechanism Each of the guide grooves is attached to the front surface of the frame at each processing position by sliding the locking piece into the locking groove. This is a transfer press designed to do this.

  The effect can be easily added to a predetermined punch driving device unitized or replaced with a predetermined punch driving device in accordance with the number of workpiece processes to be produced. Further, it is possible to easily set each pair of fingers at a holding time and a transfer time corresponding to each process or process group, and to provide each pair of fingers at unequal intervals. Furthermore, by unitizing the process alone or in units of process groups, a predetermined transfer driving device can be easily mounted even if the processing lines of the plurality of processes are non-linear. Further, when changing the vertical movement timing, vertical movement amount, elapsed speed, etc. of each knockout punch set during one cycle of each process, it can be easily changed by replacing the set values of the numerical control means. it can. Therefore, unnecessary time and labor of exchanging or adjusting the knockout punch and the drive unit can be saved.

  The transfer press of Patent Document 1 can easily add or replace each unitized drive device, can improve the versatility of the transfer press, and improves the workability and productivity of the setup change. It can be done. However, a large inertia load is generated when the moving body of the punch moving body, the finger moving body, and the knockout punch moving body switches the direction of reciprocating motion. The linear motor movable element of the drive source against this inertial load. Since the linear motor reciprocates with the moving body itself, the linear motor needs an output that is at least greater than the magnitude of the inertia load when switching the direction of each moving body. When trying to increase the speed, a larger inertial load is generated depending on the speed. However, when the device is made compact, there is a limit to the increase in the size of the linear motor. Yes.

  Further, the technique described in Patent Document 2 is modularized by a C-type frame and a slide driven by an arbitrary motion by a slide drive mechanism using a servo motor provided at the top of the C-type frame as a drive source. A press unit that integrates the slides of each press unit by connecting a plurality of press units in the work advance direction to form the press body and attaching a slide adapter plate with an integrated structure to the slide of each press unit. It is a machine. Further, the press machine is provided with a bolster that is integrated with the entire length of the press body. Further, it is disclosed that the slide drive mechanism drives a slide up and down by a ball screw and a ball nut through a power transmission means such as a timing belt using a servo motor as a drive source.

  The effect is that a mold can be attached to the entire slide adapter plate for molding, so that it is possible to form a long workpiece, which greatly improves the degree of freedom of molding, and drives the slide drive mechanism. By individually controlling the source with NC, even if the molding load acting on each slide is different, the shut height of each slide can be adjusted to be constant, and high-precision molding is possible. In addition, by using a servo motor that is NC controlled, the slide motion can be arbitrarily set. Furthermore, each press unit can be miniaturized by adopting a C-shaped frame. In addition, the C-type frames adjacent to each other in a plurality of press units are directly fixed by fixing means, or the entire length of the press body is arbitrarily set by interposing a spacer, or the pitch between processes is changed for reasons. You can also.

In the press machine of Patent Document 2, a plurality of press units modularized by a C-type frame and a slide driven by an arbitrary motion by a slide drive mechanism using a servo motor as a drive source are connected in a workpiece progressive direction. The press main body is configured, and the adjacent C-type frames of a plurality of press units are directly fixed by fixing means, or the entire length of the press main body is arbitrarily set by interposing a spacer, The pitch can be freely changed. However, when considering a press machine in which the slide is controlled independently for each process, this press machine connects a press unit composed of a C-shaped frame, and the interval between processes is changed by interposing a spacer. Therefore, there are problems that the process interval cannot be reduced due to the width of the C-shaped frame, and that frequent changes between processes cannot be easily performed. In addition, since a timing pulley and a ball screw are used in the power transmission section from the servo motor of the drive source to the slide, there is a problem that there is a limit in speeding up the mechanism.
JP-A-2002-153997, [0016], [0017], [0018], [0019], [0020], FIGS. JP-A-2001-58296, [0008], [0009], [0010], [0011], [0018], [0029], FIG. 1, FIG.

  The present invention has been made in view of such problems of the prior art, and the object of the present invention is to provide each drive unit such as a punch device, a knockout device, a transfer device, a servo motor, and a servo motor as a drive source. And a slide member that is directly moved via a crank mechanism or a cam mechanism, enabling high speed, having a compact structure, and being compatible with mounting on a machine base. The process interval and shut height can be easily changed, and the program can be controlled with a program selected to optimize the cycle motion curve of each slide member, so that it can be transferred to various types of press work without waste. The provision of a transfer press.

  In the transfer press, the invention includes a servo motor, an eccentric disk member rotated by the servo motor, and a connecting rod in which an eccentric part of the eccentric disk member and one end thereof are rotatably connected. A crank mechanism member, and a slide member that is rotatably connected to the other end of the connecting rod, linearly controlled in accordance with the angular phase of the eccentric disc member, and has a tool mounting portion at the tip and is linearly guided. A plurality of drive units having a configuration are arranged in parallel on the front surface of the machine base, and a plurality of punches attached to the respective tool attachment portions of the slide members and the punches are arranged in parallel on the bolster surface. Provided with a plurality of dies and a plurality of fingers that can be gripped corresponding to the workpieces that are sequentially pressed by the cooperation of the punch and the die. A transfer bar capable of reciprocating in the parallel arrangement direction, a transfer bar drive unit for controlling the position of the finger at each position of the punch, and the punch drive unit and the transfer bar drive unit. The main feature is that a numerical control means for performing numerical control is provided, and the workpiece is transferred from the upstream process to the downstream process in order and pressed.

  According to a second aspect of the present invention, in the transfer press, a cam mechanism member including a servo motor, a cam member rotated by the servo motor, and a cam follower driven by the cam member, and an angle of the cam member integrally with the cam follower A plurality of drive units having a linear position controlled according to the phase and having a tool mounting portion at the tip and a linearly guided slide member are arranged in parallel on the front surface of the machine base, and each of the slide members is attached to the tool. A plurality of punches attached to the part, a plurality of dies arranged in parallel on the bolster surface facing each of the punches, and a workpiece that is sequentially pressed by the cooperation of the punch and the die. A transfer bar having a plurality of fingers that can be gripped correspondingly, and capable of reciprocating in the direction in which the dies are juxtaposed, A transfer bar drive unit that controls the position of the punch bar, and numerical control means for controlling the numerical value of the punch drive unit and the transfer bar drive unit in synchronization with each other. The main feature is that it is transferred and pressed.

  According to a third aspect of the present invention, in the second aspect of the present invention, the cam curve of the cam member is a deformed constant velocity curve in which an increase in cam lift with respect to a rotation angle of the cam member in a linear motion section of the slide member is constant. This is the main feature.

  According to a fourth aspect of the present invention, in the transfer press according to the first to third aspects, the drive unit of the transfer bar has the same configuration as the drive unit of the punch, and the transfer bar is attached to a tool mounting portion at the tip of the slide member. The main feature is that it is attached.

  According to a fifth aspect of the present invention, in the transfer press according to any one of the first to fourth aspects, a knockout punch having the same configuration as the drive unit of the punch is provided behind the bolster on the opposite side of the punch of at least one die. The most important feature is that a knockout punch is attached to the tip of the slide member so as to face the punch, and the knockout punch drive unit is synchronously controlled by the numerical control means with the punch drive unit. To do.

  According to a sixth aspect of the present invention, in the transfer press according to the first to fifth aspects, each of the punch driving unit or the knockout punch driving unit is independent of the reciprocating movement direction of the punch or the parallel arrangement direction of the dies. The most important feature is that the mounting position can be changed.

  According to a seventh aspect of the present invention, in the transfer press according to any one of the first to sixth aspects, the punch drive unit, the transfer bar drive unit, and the knockout punch drive unit are compatible in mounting. Features.

  According to an eighth aspect of the present invention, in the transfer press according to the first to seventh aspects, the servo motor is a low inertia motor.

  The transfer press of the present invention has the following effects as a result of solving the problems by the above-mentioned means.

  According to the first aspect of the present invention, the rotation of the servo motor is directly converted into the linear motion of the slide member via the crank mechanism, and the speed and position of the slide member are controlled with a simple structure. Therefore, the crank rotational force is transmitted to the slide member by expanding the component force in the inertia load direction against the large inertia load generated when the direction of the reciprocating unit such as the slide member operated by the servo motor is changed. Since a small force is sufficient, it is possible to rotate at a higher speed than when a moving body is directly driven by a linear motor. In particular, in the case of continuous rotation, since there is no reciprocal switching unlike a linear motor, the speed can be remarkably increased. Furthermore, since the structure is simple, the mass of the movable part can be reduced, and further high speed rotation is possible. In addition, the punch drive units are arranged in parallel for each process, and each servo motor for each drive unit is independently numerically controlled to control each slide member with an independent motion curve according to the needs of each process. And position control and speed control can be performed with high accuracy.

  As a result, with the improvement of production speed, multiple programs corresponding to the optimal motion curve of punches suitable for machining in each process can be prepared and selected for each process or for each product type. It is possible to easily change the program to the optimal curve program, and the motion curve can be changed by changing the program, so the adjustment time can be shortened. In addition, by selecting the optimal motion curve of the punch that is suitable for the processing in each process, it is possible to improve product accuracy and reduce noise.

  According to the second aspect of the present invention, the rotation and speed of the slide member are controlled by converting the rotation of the servo motor into a linear motion of the slide member via a cam mechanism having a simple structure. Therefore, by selecting the optimal cam diagram for the large inertia load that occurs when the direction of the reciprocating part such as the slide member that operates by the servo motor is changed, the cam rotation force is increased in the inertia load direction. Therefore, since a small force is sufficient, it is possible to rotate at a higher speed than when the moving body is directly driven by a linear motor. In particular, in the case of continuous rotation, since there is no reciprocal switching unlike a linear motor, the speed can be remarkably increased. Furthermore, since the structure is simple, the mass of the movable part can be reduced, and further high speed rotation is possible. In addition, the punch drive units are arranged in parallel for each process, and each servo motor for each drive unit is independently numerically controlled to control each slide member with an independent motion curve according to the needs of each process. And position control and speed control can be performed with high accuracy.

  According to the invention of claim 3, the cam curve of the cam member is a deformation constant velocity curve in which the increase of the cam lift with respect to the rotation angle of the cam member in the linear motion section of the slide member is constant. In addition to the effect, the cam rotation angle and the amount of movement of the slide member are proportional to each other in the constant speed section, so that a program for obtaining an optimal motion curve can be easily created.

  In the invention according to claim 4, since the drive unit of the transfer bar has the same configuration as the drive unit of the punch, in addition to the effects of the invention according to claims 1 to 3, a plurality of fingers capable of gripping a workpiece are provided. The transfer bar equipped with can be reciprocated smoothly at high speed, and position control and speed control can be performed with high accuracy. As a result, high-speed rotation is possible by selecting an optimal motion curve of the transfer bar for all processes.

  According to the fifth aspect of the present invention, there is provided a knockout punch having the same configuration as that of the punch drive unit at the rear side of the bolster opposite to the punch of at least one die and having a knockout punch attached to the tool attachment portion at the tip of the slide member. Since the drive unit is provided, in addition to the effects of the first to fourth aspects, the knockout punch can be controlled in synchronization with the punch position. As a result, the engagement between the knockout and the workpiece is a smooth hit, and there is no trouble that damages or deforms the workpiece, so that the product accuracy can be improved.

  Since the punch drive unit or the knockout punch drive unit can change the mounting position independently in the reciprocating direction of the punch or in the direction in which the dies are arranged side by side, In addition to the effects of the inventions described in Items 5 to 5, when the type of the workpiece is changed, the height of the punch or knockout punch can be changed to an optimum height for the height of the workpiece. In addition, the process interval can be changed according to the size of the workpiece and the number of processes. As a result, the range of workpieces that can be processed by a single machine is expanded, equipment costs can be reduced, and setting time for workpiece replacement can be shortened.

  According to the seventh aspect of the present invention, the punch drive unit, the transfer bar drive unit, and the knockout punch drive unit are compatible in mounting. In addition, servo motors, eccentric disk members or cam members, slide members, tool holding members, etc. can be used uniformly even if there are some changes in specifications, which is effective in reducing equipment costs. In addition, each unit can be unified and can be manufactured at low cost, and the equipment cost can be reduced.

  According to the eighth aspect of the invention, since the servo motor is a low inertia motor, it is possible to quickly follow the speed change during acceleration / deceleration.

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

  1 is a front view of a transfer press according to the present invention, FIG. 2 is a cross-sectional view of AA in FIG. 1, FIG. 3 is a front view of a punch drive unit, FIG. 4 is a cross-sectional view of BB in FIG. FIG. 6 is a block diagram showing the configuration of the transfer press of the present invention, and FIG. 7 is a timing diagram in the transfer press of the present invention.

  1 and 2, a plurality of punch drive units 4 each having a punch 3 attached to the tip thereof are disposed on the front upper wall surface of the frame 1 from the left side to the right side in the workpiece transfer axis direction for each process. A die holder 5 in which a die 6 facing the punch 3 is fitted is disposed on the bolster 17 immediately below the punch 3. On the upper surface of the die holder 5, a plurality of fingers 14L and 14R capable of gripping workpieces in each process are provided, and a transfer bar 11 that moves back and forth by an inter-process pitch is disposed. A drive unit 13 for the transfer bar 11 is provided. Is attached to the left side surface of the frame 1. Immediately below the die holder 5, a knockout punch drive unit 9 having a knockout punch 8 acting from below the workpiece mounted on the tip is required to separate the pressed workpiece from the die 6 against each die 6. Each process is provided.

  The punch drive unit 4 includes a servo motor 25 (with a reduction gear if necessary), a crank mechanism member 24 including an eccentric disk member 29 and a connecting rod 34, and a slide member 31 that is linearly guided. The unit is compact. Here, the connecting rod 34 includes a connecting rod base portion 34A, a connecting rod tip portion 34B, and an adjusting shaft 37 for connecting them.

  The knockout punch drive unit 9 and the transfer bar drive unit 13 have the same configuration as the punch drive unit 4. However, in the transfer bar drive unit 13, the tool holder 33 in the punch drive unit 4 is a connecting plate 12. The punch drive unit 4 and the punch 3 attached to the tip thereof constitute the punch device 2, and the knockout punch drive unit 9 and the knockout punch 8 attached to the tip constitute the knockout device 7, and the transfer bar. The transfer unit 10 is composed of the drive unit 13 and the transfer bar 11 attached to the tip of the drive unit 13. The transfer bar 11 is provided with a pair of fingers 14R and 14L biased by a spring so as to be able to grip a workpiece for each process.

  As shown in FIG. 2, T-shaped locking grooves 1b and 1c are horizontally engraved on the mounting surface 1f of the front surface of the frame 1, and the punch drive unit 4 is disposed in the horizontal direction, that is, in the workpiece transfer axis direction. Adjustment is possible. Thereby, the process interval can be easily changed. In addition, by changing the mounting position of the punch drive unit 4 to either the lower T-shaped locking groove 1b or the upper T-shaped locking groove 1c, it is possible to easily cope with changes in workpiece height and shut height. It is also possible to do. In addition, the material supply apparatus 15 is shown in FIG. The material supply device 15 is provided on the rear surface of the machine in order to supply the material to the blanking step of the first processing step. The material is transferred from the back to the front, and the blank after blanking is collected on the front side. The drive device of the material supply device 15 is operated in synchronism with drive devices such as the punch device 2, the knockout device 7, and the transfer device 10.

  The configuration of the punch drive unit 4 will be described in detail with reference to FIGS. The punch drive unit 4 is configured with a unit base 21 as a base, and its mounting surface 21 a is fixed in contact with the mounting surface 1 f of the frame 1. A hole 21c is drilled in the upper boss portion of the unit base body 21 at right angles to the mounting surface 21a. A servomotor 25 is attached to the hole 21c by fitting its attachment portion. The servo motor 25 is preferably a low inertia servo motor. A cylindrical sleeve 26 having a step hole of a large diameter hole and a small diameter hole is fitted to the output shaft 25a of the servo motor 25. The small diameter hole is fitted to the output shaft 25a, and between the large diameter hole and the output shaft 25a. It is fixed by attaching a fastening ring 27 for fastening the inside and outside using a wedge action.

  The sleeve 26 is rotatably supported by a bearing 28 that fits into a hole 21c that is formed in the upper boss portion perpendicular to the mounting surface 21a of the unit base 21. An eccentric disc 29 having a protruding shaft portion 29a protruding outward at an eccentric position is mounted on the end surface of the sleeve 26 on the large-diameter hole side. One end of a connecting rod base portion 34A is rotatably connected to the protruding shaft portion 29a. The other end of the connecting rod base portion 34A is connected to a connecting rod tip portion 34B via an adjustment shaft 37 to form a connecting rod 34. The length of the connecting rod 34 can be adjusted by rotating the adjusting shaft 37 to position the forward end of the punch 3 and then tightening and locking the respective slits with bolts 38. The eccentric disc 29 and the connecting rod 34 constitute a crank mechanism member 24.

  The distal end of the connecting rod tip 34B is rotatably connected to a fulcrum shaft 35 provided on the slide member 31 so as to be orthogonal to the moving direction. A tool holder 33 in which a hole in the moving direction of the slide member 31 is formed is attached to the distal end portion of the slide member 31. In this hole of the tool holder 33, the punch 3 is inserted and protruded in the moving direction of the slide member 31 and fixed. The punch 3 attached to the tool holder 33 includes a blanking punch, a drawing punch, a punching punch, a forming punch, a trimming punch, and the like.

  A guide key 22 is press-fitted and attached to the unit base 21 on the attachment surface 21a on the back surface thereof in the workpiece transfer direction. On the other hand, T-shaped locking grooves 1b and 1c into which a guide key 22 is slidably guided in the workpiece transfer direction and a T-nut 23 can be inserted are formed on the mounting surface 1f of the frame 1. The unit base 21 has a mounting surface 21 a abutting against a mounting surface 1 f of the frame 1 and is fixed by a bolt 16. Therefore, the mounting position of the unit base 21 can be changed along the T-shaped locking groove 1b or 1c in the workpiece transfer direction, and the T-shaped locking is engraved in two rows on the mounting surface 1f of the frame 1 respectively. By selecting the groove 1b or 1c, the mounting position in the vertical direction can be changed.

  A lower guide plate 30 is attached to the front surface 21 d of the unit base 21, and a guide groove 30 a is formed on the front side of the lower guide plate 30 so that the slide member 31 can linearly reciprocate in the longitudinal direction of the unit base 21. . The left and right blade surfaces of the slide member 31 are slidably guided by the guide groove 30a of the lower guide plate 30 and the upper guide plates 32R and 32L.

  By attaching the knockout punch 8 in place of the punch 3 attached to the tool holder 33, the knockout device 7 can be used. That is, in FIG. 2, a knockout device 7 including a knockout punch 8 facing the die 6 and a knockout punch driving unit 9 is attached to the lower portion of the front wall 1 g of the frame 1. Thus, the knockout punch drive unit 9 has the same configuration as the punch drive unit 4.

  Moreover, it can replace with the tool holder 33 and the punch 3, and can be used as the transfer apparatus 10 by attaching the connection board 12 and the transfer bar 11. FIG. FIG. 5 shows a case where the punch drive unit 4 is applied to the transfer bar drive unit 13 constituting the transfer apparatus 10. The transfer device 10 is a device that moves a work by a pitch between steps in the work movement axis direction, and is driven by a transfer bar 11 provided on a die holder 5 that is guided by a guide (not shown) and can be moved forward and backward. It is comprised with the drive unit 13 of the transfer bar. The transfer bar 11 is provided with a pair of fingers 14 </ b> R and 14 </ b> L that are biased by springs so as to be able to grip a workpiece on the die 6 for each process.

  A portion of the transfer bar drive unit 13 attached to the frame 1 is shared with a portion of the punch drive unit 4 attached. The slide member 31 of the transfer bar drive unit 13 and the transfer bar 11 are connected by a connecting plate 12. Although it is necessary to select and attach the eccentric disk 29 in accordance with the stroke of the forward / backward movement of the transfer bar 11, it is possible to replace the punch drive unit 4 with the transfer bar drive unit 13. Both drive units have the same configuration.

  Next, the relationship between the configuration of the drive unit and the numerical control means C will be described with reference to the block diagram FIG. Machining conditions such as the speed, position, and work time of the punch 3, knockout punch 8 and transfer bar 11 by each drive unit are input in advance by the program input unit C1 of the numerical control means C. In actual machining, signals generated by the program reading unit C2, the program analysis unit C3, the function generation unit C4, etc. are output to the feeder control unit C5, punch control unit C6, knockout control unit C7, and transfer control unit C8. These control units output a control command to each servo motor 25 of each drive unit.

  Next, the operation of each drive unit will be described with reference to FIG. The diagrams of the punch 3 and the knockout punch 8 show typical motion curves. In the implementation, several types of motion curves are prepared for each process as needed, and can be selected from them. The horizontal axis of FIG. 7 shows the angular position (hereinafter referred to as the press angle) obtained by dividing one cycle of the transfer press into 360 equal parts, and the vertical axis shows the displacement of each tool of the punch 3, the knockout punch 8 and the transfer bar 11, respectively. The displacements of the punch 3, the knockout punch 8 and the transfer bar 11 are read at a position corresponding to the press angle set by the program by reading the program corresponding to the workpiece from the program input in advance in the program input C1 shown in FIG. is there.

  In FIG. 7, when the transfer press is activated, first, in the first step, the punch 3 descends from a press angle of 20 degrees to 160 degrees, performs blanking, and rises after stopping at the bottom dead center until the press angle is 190 degrees. To do. The processed workpiece is gripped by the fingers 14R and 14L of the transfer bar 11 at a press angle of 250 to 350 degrees and transferred to the second step. In this first step, not only blanking processing but also drawing processing may be performed at the same time, so-called blanking processing may be performed. In the second step of the next cycle, the punch 3 descends from a press angle of 20 degrees to 160 degrees and performs a drawing process in cooperation with the die 6. At this time, the transfer bar 11 is stopped at the right feed position when the press angle is between 0 degrees and 120 degrees. The knockout punch 8 descends while holding the workpiece together with the punch 3 at the rising end when the press angle is between 0 degrees and 90 degrees and between 90 degrees and 160 degrees.

  During this time, the transfer bar 11 moves backward from the press angle of 120 ° to 200 ° while leaving the workpiece being processed, and the plurality of sets of fingers 14L and 14R move to the workpiece positions in the previous process. The punch 3 rises from a press angle of 190 degrees to 270 degrees, and on the way, leaves the workpiece and reaches top dead center. The knockout punch 8 rises while holding the workpiece from the bottom as the punch 3 rises while the press angle reaches 190 degrees to 240 degrees. When the lower surface of the workpiece reaches the upper surface of the die 6, the workpiece is gripped by the fingers 14L and 14R. Is done.

  The transfer bar 11 stops at the left return position during a press angle of 200 degrees to 250 degrees. The punch 3 is at the top dead center between the press angles of 270 ° and 360 °, and the knockout punch 8 is at the rising end between the press angles of 240 ° and 360 °. The transfer bar 11 transfers the work gripped by the fingers 14L and 14R to the next process at a press angle of 250 to 350 degrees. Similar operations are repeated in the next step of the next cycle. The workpieces that are sequentially processed in this way are transferred to the next step, and further processed in the next step, and this operation is repeated simultaneously for each step to continuously produce the workpiece.

  The lowering / raising of the punch 3 and the knockout punch 8 and the left return / right feeding operations of the transfer bar 11 are controlled in speed and position by numerically controlling the servo motors 25 by the numerical control means C. 3 and the knockout punch 8 are controlled by an optimal motion curve for each process. That is, the eccentric disk 29 provided directly connected to the output shaft 25a of the servo motor 25 of each drive unit is controlled by the numerical control means C for one rotation, and the speed and position of each device are controlled by the optimum motion curve. doing. In addition, a plurality of programs for obtaining an optimal motion curve for each type of work are prepared, and the optimum machining conditions can be selected by selecting from these programs.

  Next, the operation of the transfer press according to the first embodiment of the present invention will be described. As described above, each drive unit of the punch device 2, the knockout device 7, and the transfer device 10 includes the servo motor 25 (with a speed reducer if necessary), the crank mechanism member 24 including the eccentric disk member 29 and the connecting rod 34, and the direct drive unit. The slide member 31 that is guided by movement is compactly configured and unitized. That is, each drive unit directly converts the rotation of the servo motor 25 into a linear motion of the slide member 31 via the crank mechanism member 24 to control the position and speed of the slide member 31. Therefore, when the direction of reciprocation of the slide member 31 is switched, the crank rotational force for rotating the eccentric disk member 29 to which the connecting rod 34 is connected is inertial although the inertial load increases rapidly. Since the component force in the load direction is expanded and transmitted as reciprocating power to the slide member 31, it is possible to reciprocate the slide member 31 with a small crank rotational force, unlike when the slide member is directly reciprocated with a linear motor. It becomes. Therefore, the slide member 31 can be reciprocated linearly at high speed even with a small-capacity servo motor 25 having a small mounting space compared to a linear motor. Furthermore, since the structure is simple, the mass of the movable part can be reduced, and the reciprocating movement can be performed smoothly at high speed. Further, if the servo motor 25 is a low inertia servo motor, it is possible to promptly follow the speed change at the time of acceleration / deceleration of the slide member 31 and further increase the speed.

  When the eccentric disk member 29 is continuously rotated, there is a further flywheel effect of the rotating portion, and the slide member 31 can be smoothly reciprocated under the best conditions to enable high-speed rotation. Further, even when the eccentric disc member 29 is temporarily stopped at the moving end (bottom dead center or top dead center) of the slide member 31 without continuously rotating, the eccentric disc member 29 is moved at this angular position. Since the crank rotational force is most enlarged and transmitted to the slide member 31 as a component force for reciprocating linear motion, even if the crank rotational force is smaller than that of the linear motor, that is, the servo motor 25 has a smaller capacity, High speed rotation is possible.

As shown in FIG. 1, the punch drive unit 4 or the knockout punch drive unit 9 is arranged in the horizontal direction, that is, in the workpiece transfer axis direction by the T-shaped locking grooves 1b, 1c or 1d, 1e of the frame 1. Is adjustable. Thereby, the process interval can be easily changed. Also, by changing the mounting position of the punch drive unit 4 between the lower T-shaped locking groove 1b and the upper T-shaped locking groove 1c, it is possible to easily cope with changes in the work height and the shut height. Is also possible. Also, by changing the mounting position of the knockout punch drive unit 9 between the lower T-shaped locking groove 1e and the upper T-shaped locking groove 1d, it is possible to easily cope with the change in workpiece height. is there. The punching device 2 and the knockout device 7 can be equipped with a number of drive units installed in the same frame 1 according to the number of press work steps, and several types of units such as units with different outputs of the servo motor 25 are prepared. In addition, the drive unit can be replaced according to the load. The transfer bar drive unit 13 can be replaced with the punch drive unit 4 or the knockout punch drive unit 9 as necessary by exchanging some parts.

  Further, the position and speed of the slide member 31 can be controlled by numerically controlling the servo motor 25 according to the rotation angle of the transfer press. Since the control circuit of the servo motor 25 of the punch drive unit 4 is provided independently, if various programs are input in advance so as to obtain an optimum motion curve, the optimum program is selected from them. In addition, the optimal motion curve can be selected for each process, making it easy to respond to workpiece changes. Since the style of the servo motor 25 is unified, it is possible to quickly respond to machining program changes and maintenance.

  By applying the basic configuration of the punch drive unit 4 to the knockout punch drive unit 9, the drive unit can be shared and the control system of the servo motor 25 can be easily designed. By optimally selecting the motion curve of the knockout punch 8 in relation to the punch drive unit 4, the engagement between the workpiece and the punch 3 or the knockout punch 8 becomes smooth. Therefore, deformation of the workpiece can be prevented and noise during blanking can be reduced.

  8 is a front view of a punch drive unit including a cam mechanism member 48, and FIG. 9 is a CC cross-sectional view of FIG. The second embodiment relates to a transfer press in which the crank mechanism member 24 of the first embodiment is replaced with a cam mechanism member 48 to constitute a punch unit, a knockout device, and a drive unit of the transfer device. Accordingly, since the configuration and operation of the invention of FIGS. 1 to 7 described in the first embodiment are mostly the same, only the differences between FIGS. 8 and 9 corresponding to FIGS. 3 and 4 will be described here. explain.

  A flange 42 is attached to the end face of the sleeve 26 attached to the output shaft 25a of the servo motor 25 by bolts. A groove cam 43 is attached to the flange 42 by a bolt. A cam follower 45 attached to one side of the cam follower body 46 is engaged with the cam groove of the groove cam 43, and a slide member 47 is attached to the other end of the cam follower body 46 via an adjustment shaft 37. The slide member 47 is slidably guided on the left and right blade surfaces by the guide groove 30a of the lower guide plate 30 attached to the front surface 21d of the unit base 21 and the upper guide plates 32R and 32L. Follow and reciprocate linearly. The tool holder 33 fastened to the slide member 47 is provided with a punch 3 protruding in the longitudinal direction of the unit base 21.

  The cam follower body 46 and the slide member 47 are screwed together and connected to an adjustment shaft 37 having left and right threads formed at both ends. By rotating the adjustment shaft 37, the lower end position of the punch 3 can be adjusted.

  The cam curve of the groove cam 43 is formed as a constant velocity curve in which the increase in the cam lift with respect to the cam rotation angle is constant in the linear motion section, and a relaxation curve that softens the impact in response to a change in acceleration before and after the linear motion section. It is the deformation constant velocity curve formed. Further, if necessary, it may be formed so that the cam lift with respect to the rotation angle of the cam becomes 0 continuously with the relaxation curve, and the top dead center or the bottom dead center portion may be formed. As the cam curve, an optimum cam curve other than the deformation constant velocity curve may be selected as necessary. In order to obtain high-speed rotation, the pressure angle is desirably 30 degrees or less. As for the knockout device and the transfer device, their drive units have the same configuration as the drive unit of the punch device, and are compatible.

  The operation of the second embodiment will be described. The punch drive unit including the cam mechanism member 48 converts the rotation of the servo motor 25 into a linear motion of the slide member 47 via the cam mechanism member 48, and controls the speed and position of the slide member 47. Yes. The pressure angle of the cam is 30 degrees or less. Therefore, when the rotation of the groove cam 43 rotated by the servo motor 25 is converted into the reciprocal linear motion of the slide member 48 by the cam mechanism, the linear force acting on the slide member 48 is the inertial load of the rotational force. Since the component force in the direction is enlarged and transmitted, the slide member 31 can be reciprocated with a smaller cam rotational force than when the slide member is directly reciprocated by the linear motor. Therefore, even with a small-capacity servo motor 25 with a small mounting space, the slide member 31 can be reciprocated linearly at a higher speed than in the case of a linear motor. Furthermore, since the structure is simple, the mass of the movable part is reduced, and the reciprocating movement can be performed smoothly at high speed. Further, if the servo motor 25 is a low inertia servo motor, the speed can be further increased.

  Further, since the deformation constant velocity curve is used, in the linear motion section, the rotation angle of the groove cam 43 and the movement amount of the slide member 47 are in a proportional relationship. Therefore, it becomes easy to keep the straight moving speed of the linear movement section of the slide member 47 constant. In addition, it is easy to create a program for obtaining an optimal motion curve by numerically controlling the speed and position of the slide member 47 with respect to the rotation angle of the servo motor 25. In addition, since the control circuit for the servo motor 25 is provided independently, an optimal motion curve can be selected and input for each process, and it can be immediately adapted to production of other types, which is effective in improving productivity. In addition, since the servo motor 25 has a unified format, it is possible to quickly respond to machining program changes and maintenance. Since the drive unit of the knockout device and transfer device has the same configuration as the drive unit of the punch device, the same operation and effect are obtained. The transfer press according to the present invention is not limited to the embodiment described above, and can be configured in various forms without departing from the gist of the present invention.

It is a front view of the transfer press in Example 1 of the present invention. It is AA sectional drawing of FIG. It is a front view of the punch drive unit in Example 1. FIG. It is BB sectional drawing of FIG. It is DD arrow line view of FIG. 1 is a block diagram illustrating a configuration of a transfer press in Embodiment 1. FIG. 3 is a timing diagram of a transfer press in Embodiment 1. FIG. It is a front view of the punch drive unit in Example 2. It is CC sectional drawing of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Frame 2 Punch device 3 Punch 4 Punch drive unit 5 Die holder 6 Die 7 Knockout device 8 Knockout punch 9 Knockout punch drive unit 10 Transfer device 11 Transfer bar 12 Connecting plate 13 Transfer bar drive unit 14R, 14L Finger 15 Material supply Device 17 Bolster 21 Unit base 22 Guide key 23 T nut 24 Crank mechanism member 25 Servo motor 26 Sleeve 27 Fastening ring 28 Bearing 29 Eccentric disk 30 Lower guide plate 31, 47 Slide member 32R, 32L Upper guide plate 33 Tool holder 34 Connecting Rod 34A Connecting rod base 34B Connecting rod tip 35 Support shaft 37 Adjustment shaft 38 Bolt 42 Flange 43 Groove cam 45 Cam shaft Lower 46 cam follower member 48 the cam mechanism member

Claims (8)

A crank mechanism member comprising a servo motor, an eccentric disc member rotated by the servo motor, an eccentric portion of the eccentric disc member, and a connecting rod having one end rotatably connected thereto; and the other end of the connecting rod A plurality of drive units on the front surface of the machine base that are rotatably connected to each other and linearly controlled in accordance with the angular phase of the eccentric disk member, and having a tool mounting portion at the tip portion and linearly guided. Side by side,
A plurality of punches attached to each of the tool attachment portions of the slide member; a plurality of dies arranged in parallel on the bolster surface facing each of the punches;
A transfer bar that includes a plurality of fingers that can be gripped corresponding to each workpiece that is sequentially pressed by the cooperation of the punch and the die, and that can reciprocate in the direction in which the dies are juxtaposed. A transfer bar drive unit that controls the position of
A transfer press that includes a numerical control unit that performs numerical control of the punch driving unit and the transfer bar driving unit in synchronization, and transfers a workpiece from an upstream process to a downstream process to perform press processing. A cam mechanism member composed of a servo motor, a cam member rotated by the servo motor, and a cam follower driven by the cam member, and linear position control according to the angular phase of the cam member integrated with the cam follower is performed at the tip portion. A plurality of drive units composed of a slide member that has a tool mounting portion and is linearly guided are arranged in parallel on the front surface of the machine base,
A plurality of punches attached to each of the tool attachment portions of the slide member; a plurality of dies arranged in parallel on the bolster surface facing each of the punches;
A transfer bar that includes a plurality of fingers that can be gripped corresponding to each workpiece that is sequentially pressed by the cooperation of the punch and the die, and that can reciprocate in the direction in which the dies are juxtaposed. A transfer bar drive unit that controls the position of
A transfer press that includes a numerical control unit that performs numerical control of the punch driving unit and the transfer bar driving unit in synchronization, and transfers a workpiece from an upstream process to a downstream process to perform press processing. The transfer press according to claim 2, wherein the cam curve of the cam member is a deformed constant velocity curve in which an increase in cam lift with respect to a rotation angle of the cam member in a linear motion section of the slide member is constant. 4. The transfer according to claim 1, wherein the transfer bar drive unit has the same configuration as the punch drive unit, and the transfer bar is attached to a tool attachment portion at a tip end portion of the slide member. 5. press. A knockout punch drive unit having the same configuration as that of the punch drive unit is provided behind the bolster on the opposite side of the punch of at least one die, and the slide member is opposed to the punch at the tip of the slide member. The transfer press according to any one of claims 1 to 4, wherein a punch is attached, and the knockout punch drive unit is synchronously controlled by the numerical control means with the punch drive unit. 6. The punch drive unit or the knock-out punch drive unit can be independently mounted in a different position in the reciprocating direction of the punch or in the direction in which the dies are arranged side by side. Transfer press as described in 1. The transfer press according to any one of claims 1 to 6, wherein the punch drive unit, the transfer bar drive unit, and the knockout punch drive unit are compatible in mounting. The transfer press according to claim 1, wherein the servo motor is a low inertia motor.