stamping machinery

Abstract

The present invention provides a stamping machine that simplifies the drive mechanism of the slider. The stamping machine includes: a slider (16) supported for reciprocating movement; a crankshaft (32) arranged along the length direction of the slider (16) and having a plurality of eccentric portions; a drive unit (36) that rotates the crankshaft (32); a plurality of yokes (34A, 34B) arranged at each eccentric portion of the crankshaft (32), and the plurality of yokes (34A, 34B) reciprocating along the movement direction of the slider (16) by the rotation of the crankshaft (32); and a plurality of force points (30A to 30D) that connect each yoke (34A, 34B) to the slider (16), at least one yoke (34A, 34B) being connected to the slider (16) via the plurality of force points (30A to 30D) arranged in a direction orthogonal to the axial direction of the crankshaft (32).

Description

Technical Field

[0001] This invention relates to press machines, and more particularly to press machines with structures that apply pressure to a slider at multiple points. Background Technology

[0002] Mainly, in large-scale stamping machinery, a structure is adopted in which multiple pressure points are configured on the slider, and pressure is applied to the slider at multiple points.

[0003] In stamping machines that apply pressure to a slider by arranging multiple points of force along the length direction of the slider and in directions orthogonal to the length direction, multiple crankshafts have conventionally been used to form the slider drive mechanism (e.g., Patent Documents 1, 2, etc.).

[0004] Prior art literature

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Application Publication No. 2006-61974

[0007] Patent Document 2: Japanese Patent Application Publication No. 2001-121297

[0008] However, when multiple crankshafts are used in the drive mechanism of the slider, there are disadvantages such as the drive mechanism becoming complex and large. Summary of the Invention

[0009] The problem that the invention aims to solve

[0010] The present invention was made in view of this situation, and its purpose is to provide a stamping machine that simplifies the drive mechanism of the slider.

[0011] Solution for solving the problem

[0012] (1) A stamping machine comprising: a slider supported for reciprocating movement; a crankshaft disposed along the length direction of the slider and having a plurality of eccentric portions; a drive unit for rotating the crankshaft; a plurality of yokes disposed at each of the eccentric portions of the crankshaft and reciprocating along the movement direction of the slider by rotation of the crankshaft; and a plurality of force points connecting each yoke to the slider, wherein at least one yoke is connected to the slider via a plurality of force points disposed in a direction orthogonal to the axial direction of the crankshaft.

[0013] According to this solution, by employing a so-called anti-rotation yoke mechanism, a structure can be implemented using a single crankshaft to apply pressure to the slider by arranging multiple force points along the slider's length direction and in directions orthogonal to the length direction. This simplifies the slider's drive mechanism. Furthermore, by employing the anti-rotation yoke mechanism, the slider's drive mechanism can be made more compact. That is, since the anti-rotation yoke mechanism does not suffer from the tilting effect based on the link ratio as in drive mechanisms using connecting rods, the length of the connection between the yoke and the force points can be shortened. This allows for compactness in the vertical direction (the slider's direction of movement). Additionally, this also reduces the moment of inertia of the drive system.

[0014] (2) According to (1) the stamping machine, wherein the crankshaft has eccentric portions at at least both ends in the axial direction, and the yokes provided at the eccentric portions at both ends in the axial direction of the crankshaft are connected to both ends in the length direction of the slider via a plurality of force points arranged in a direction orthogonal to the axial direction of the crankshaft.

[0015] According to this design, yokes are provided at least at both ends of the crankshaft. Furthermore, the yokes at these ends are connected to both ends of the slider along its length via multiple points of force application. This allows for more stable pressure application to the slider.

[0016] (3) According to (2) the stamping machine, wherein the crankshaft has an eccentric portion between the eccentric portions at both ends of the axial direction, and the yoke equipped with the eccentric portion between the eccentric portions at both ends of the axial direction of the crankshaft is connected to the slider via a point of force.

[0017] According to this design, a yoke is also provided at a position between the two ends of the crankshaft (e.g., at the center). Furthermore, this yoke is connected to the slider via a point of force application. This suppresses slider deflection. Additionally, this reduces slider rigidity and allows for a more compact vertical dimension of the slider. Furthermore, it reduces the moment of inertia of the drive system.

[0018] (4) A stamping machine according to any one of (1) to (3), wherein the drive unit comprises: a main gear mounted on a crankshaft; a pinion meshing with the main gear; and a motor that causes the pinion to rotate.

[0019] According to this design, the drive unit includes: a main gear mounted on a crankshaft; a pinion gear meshing with the main gear; and a motor that rotates the pinion gear. When the motor is driven, its rotation is transmitted to the main gear via the pinion gear, causing the main gear to rotate. Thus, the rotation of the main gear rotates the crankshaft.

[0020] (5) According to (4) the stamping machine, in which multiple small gears mesh with the main gear and the main gear is driven by multiple motors.

[0021] According to this scheme, multiple pinions mesh with a single main gear, and the main gear is driven by multiple motors. By meshing multiple pinions with a single main gear, the transmitted torque at each meshing point of the gears can be reduced. This allows for a reduction in the tooth width of the main gear. Furthermore, this reduces the moment of inertia of the main gear.

[0022] (6) The stamping machine according to (4) or (5), wherein the main gear is equipped at multiple positions on the crankshaft.

[0023] According to this design, the main gears are positioned at multiple locations on the crankshaft. This reduces the transmitted torque of each main gear. It also allows for a reduction in the tooth width of the main gears. Furthermore, it reduces the moment of inertia of the main gears.

[0024] (7) A stamping machine according to any one of (4) to (6), wherein the motor is arranged axially along the crankshaft.

[0025] According to this solution, the motor's orientation can be aligned with the length direction of the slider. This allows for the compact mounting of a motor with a large axial dimension.

[0026] (8) A stamping machine according to any one of (1) to (7), wherein the stamping machine further comprises a control unit for controlling the drive of the drive unit, the control unit controlling the drive of the drive unit in such a way that the slider stays at or near the top dead center for a certain period of time in each cycle.

[0027] According to this solution, the drive unit is driven such that the slider remains at or near the top dead center for a certain period of time in each cycle. This ensures efficient workpiece loading and unloading time and shortens the slider's stroke. Furthermore, this shortens the length of the connection between the yoke and the point of force application, reducing the moment of inertia of the drive system.

[0028] (9) According to (8) the stamping machine, wherein the control unit performs a drive to stop or decelerate the rotation of the crankshaft at or near the top dead center of the slider.

[0029] According to this scheme, by controlling the rotation of the crankshaft (driven by the motor), it is possible to make the slider stay at or near the top dead center for a certain period of time in each cycle.

[0030] Invention Effects

[0031] According to the present invention, in a stamping machine with a structure that applies pressure to the slider at multiple points, the slider driving mechanism can be simplified. Attached Figure Description

[0032] Figure 1This is a partial front sectional view showing one embodiment of a stamping machine to which the present invention is applied.

[0033] Figure 2 This is a partial sectional view of a side view showing an embodiment of a stamping machine to which the present invention is applied.

[0034] Figure 3 This is a top view of the slider.

[0035] Figure 4 This is a front sectional view showing the outline structure of the slider drive mechanism.

[0036] Figure 5 yes Figure 4 Sectional view 5-5.

[0037] Figure 6 yes Figure 4 Sectional view 6-6.

[0038] Figure 7 This is a partial sectional view of a plan view showing the general structure of the slider drive mechanism.

[0039] Figure 8 This is a diagram showing the change in the state of the slider when the crank is rotated one revolution.

[0040] Figure 9 This is a partial front sectional view of one embodiment of a stamping machine that shows a structure in which pressure is applied to the slider at five points.

[0041] Figure 10 This is a partial sectional view of the side of a stamping machine showing an embodiment of a structure in which pressure is applied to the slider at five points.

[0042] Figure 11 yes Figure 9 as well as Figure 10 The diagram shows a top view of the slide block of the stamping machine.

[0043] Figure 12 This is a front sectional view showing the outline structure of the slider drive mechanism.

[0044] Figure 13 yes Figure 12 Sectional view 13-13.

[0045] Figure 14 It is a graph showing the movement of the slider in one cycle.

[0046] Explanation of reference numerals in the attached figures

[0047] 10… Stamping machine, 12… Frame, 14… Pad, 16… Slide, 18… Slide drive mechanism, 20… Base, 20A… Upper surface, 22… Column, 24… Crown, 24A… Motor mounting part, 24B… Motor mounting part, 26… Slide guide, 30A… Point of force (first point of force), 30B… Point of force (second point of force), 30C… Point of force (third point of force), 30D… Point of force (fourth point of force), 30E… Point of force (fifth point of force), 32… Crankshaft, 32A… Crank pin (first crank pin), 32B… Crank pin (second crank pin), 32C… Crank pin (third crank pin), 34A… Yoke (first yoke), 34B… Yoke (second yoke), 34C… Yoke (third yoke), 36… Drive part, 3 8…shaft support, 40A…yoke body, 40B…yoke body, 40C…yoke body, 42A…opening, 42B…opening, 42C…opening, 44A1…connecting part, 44A2…connecting part, 44B1…connecting part, 44B2…connecting part, 44C…connecting part, 46A…guide rail, 46B…guide rail, 46C…guide rail, 48A…bearing part, 48B…bearing part, 48C…bearing part, 50A…opening, 50B…opening, 50C…opening, 52A…main gear, 52B…main gear, 54A1…motor, 54A2…motor, 54B1…motor, 54B2…motor, 56A1…pinion, 56A2…pinion, 56B1…pinion, 56B2…pinion, 60…control part. Detailed Implementation

[0048] Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

[0049] First Implementation Method

[0050] [Device Structure]

[0051] Figure 1 , Figure 2 These are, respectively, a partial front sectional view and a partial side sectional view illustrating an embodiment of a stamping machine applying the present invention. It should be noted that... Figure 1 as well as Figure 2 In this diagram, the direction indicated by reference numeral x is taken as the horizontal direction of the device, the direction indicated by reference numeral y is taken as the front-back direction of the device, and the direction indicated by reference numeral z is taken as the vertical direction of the device.

[0052] The stamping machine 10 of this embodiment is a stamping machine with a structure that applies pressure to the slider at four points. For example... Figure 1 as well as Figure 2 As shown, the stamping machine 10 includes a frame 12, a pad 14, a slider 16, and a slider drive mechanism 18.

[0053] Frame 12 is a so-called double-column frame and includes a base 20, columns 22, and a crown 24. The base 20, columns 22, and crown 24 are integrally assembled via tie rods (not shown).

[0054] The base 20 serves as the base for bearing the stamping pressure. The upper surface 20A of the base 20 forms a horizontal plane. A pad 14 is provided on the upper surface 20A of the base 20.

[0055] The columns 22 are provided at the four corners of the base 20. Each column 22 is arranged perpendicularly to the upper surface 20A of the base 20.

[0056] Crown 24 is mounted on the upper end of post 22. As will be described later, slider drive mechanism 18 is mounted on crown 24.

[0057] The base plate 14 is a platform for mounting the mold. As described above, the base plate 14 is provided on the upper surface 20A of the machine base 20.

[0058] Slider 16 is the part on which the mold is mounted and reciprocates. For example... Figure 1 As shown, the slider 16 of this embodiment has a shape with a lateral length that is larger in the lateral direction than in the front-back direction. Therefore, the lateral direction (x-direction) is the length direction of the slider 16. The slider 16 is supported by the slider guide 26 provided on the post 22 so that it can slide freely in the vertical direction (reciprocate freely).

[0059] Figure 3 This is a top view of the slider.

[0060] As shown in the figure, the upper surface of the slider 16 has four pressure points 30A to 30D. These pressure points 30A to 30D are the connection points between the slider 16 and the slider drive mechanism 18. Therefore, the positions of these pressure points 30A to 30D become the pressure points of the slider 16. Figure 3 As shown, in the slider 16 of this embodiment, force points 30A to 30D are arranged at the four corners of the upper surface. Hereinafter, as needed, force point 30A is designated as the first force point 30A, force point 30B as the second force point 30B, force point 30C as the third force point 30C, and force point 30D as the fourth force point 30D, thereby distinguishing each force point 30A to 30D.

[0061] like Figure 3As shown, the first force point 30A and the second force point 30B are arranged along the front-rear direction of the slider 16. Similarly, the third force point 30C and the fourth force point 30D are arranged along the front-rear direction of the slider 16. In addition, the first force point 30A and the third force point 30C are arranged along the lateral direction of the slider 16. Similarly, the second force point 30B and the fourth force point 30D are arranged along the lateral direction of the slider 16. That is, in the stamping machine 10 of this embodiment, the force points 30A to 30D are arranged at multiple positions in the length direction of the slider 16 and in directions orthogonal to the length direction.

[0062] At each point of application 30A to 30D, a slider adjustment mechanism and an overload safety device are provided as needed. These mechanisms are well-known structures, therefore details thereof are omitted.

[0063] The slider drive mechanism 18 converts the rotational motion of the motor into reciprocating motion, thereby actuating the slider. As described above, the slider drive mechanism 18 is mounted on the crown 24 of the frame 12.

[0064] Figure 4 This is a front sectional view showing the outline structure of the slider drive mechanism. Figure 5 yes Figure 4 Sectional view 5-5. Figure 6 yes Figure 4 Sectional view 6-6. Figure 7 This is a partial sectional view of a plan view showing the general structure of the slider drive mechanism.

[0065] The slider drive mechanism 18 mainly includes a crankshaft 32, two yokes 34A and 34B that convert the rotational motion of the crankshaft 32 into reciprocating motion, and a drive unit 36 ​​that rotates the crankshaft 32.

[0066] The crankshaft 32 has crank pins 32A and 32B at two axial positions. More specifically, it has crank pins 32A and 32B at both axial ends. Crank pins 32A and 32B are examples of eccentric portions. Hereinafter, one crank pin 32A will be designated as the first crank pin 32A, and the other crank pin 32B as the second crank pin 32B, to distinguish between the two. The crankshaft 32 is rotatably supported by a plurality of shaft support portions 38 provided on the crown portion 24 via bearings (not shown). The crankshaft 32 supported on the shaft support portions 38 is arranged along the length direction (lateral direction of the device) of the slider 16. In addition, the crankshaft 32 is arranged at the central position in the front-rear direction of the slider 16.

[0067] Two yokes 34A and 34B are respectively positioned at the locations of the two crank pins 32A and 32B on the crankshaft 32. That is, one yoke 34A is positioned at the location of the first crank pin 32A, and the other yoke 34B is positioned at the location of the second crank pin 32B.

[0068] In the stamping machine 10 of this embodiment, the two yokes 34A and 34B have the same structure. Hereinafter, as needed, one yoke 34A will be designated as the first yoke 34A, and the other yoke 34B will be designated as the second yoke 34B, thereby distinguishing the two.

[0069] The yokes 34A and 34B have: yoke bodies 40A and 40B; two connecting portions 44A1, 44A2, 44B1, and 44B2 extending from the yoke bodies 40A and 40B; guide rails 46A and 46B, which are fitted into the openings 42A and 42B of the yoke bodies 40A and 40B; and bearing portions 48A and 48B, which slide along the guide rails 46A and 46B within the openings 42A and 42B of the yoke bodies 40A and 40B.

[0070] The yoke bodies 40A and 40B have a rectangular flat plate shape and rectangular openings 42A and 42B in the central portion. Guide rails 46A and 46B are provided along the upper and lower edges of the openings 42A and 42B. The guide rails 46A and 46B are along the front-back direction of the slider 16. Figure 5 (In the y-direction) it is configured horizontally.

[0071] In the first yoke 34A, the two connecting parts 44A1 and 44A2 are connected to the two front and rear force points 30A and 30B of the slider 16. Therefore, the two connecting parts 44A1 and 44A2 of the first yoke 34A are arranged at the same interval as the front and rear force points 30A and 30B (the first force point 30A and the second force point 30B).

[0072] In the second yoke 34B, the two connecting parts 44B1 and 44B2 are connected to the front and rear force points 30C and 30D of the slider 16. Therefore, the two connecting parts 44B1 and 44B2 of the second yoke 34B are arranged at the same interval as the front and rear force points 30C and 30D (the third force point 30C and the fourth force point 30D).

[0073] It should be noted that the interval between the third point of force 30C and the fourth point of force 30D is the same as the interval between the first point of force 30A and the second point of force 30B.

[0074] Bearing portions 48A and 48B are connected to the crankshaft 32. Bearing portions 48A and 48B have a rectangular, flat plate shape and have openings 50A and 50B in the central portion serving as bearings. Bearing portions 48A and 48B are disposed within the openings 42A and 42B of the yoke bodies 40A and 40B, and are supported to slide freely along guide rails 46A and 46B within the openings 42A and 42B. As described above, guide rails 46A and 46B are horizontally arranged along the front-rear direction of the slider 16. Therefore, bearing portions 48A and 48B slide horizontally along the front-rear direction of the slider 16 within the openings 42A and 42B. The openings 50A and 50B of the bearing portions 48A and 48B have shapes corresponding to the external shape of the crank pins 32A and 32B; that is, they have circular shapes. Bearing parts 48A and 48B are connected to crankshaft 32 by fitting crank pins 32A and 32B into openings 50A and 50B.

[0075] The yokes 34A and 34B, configured as described above, are connected to the points of force 30A, 30B, 30C, and 30D via connecting parts 44A1, 44A2, 44B1, and 44B2, thereby connecting to the slider 16. Furthermore, by connecting to the slider 16, the direction of movement is restricted to the direction of movement of the slider 16, i.e., the up-down direction. As a result, when the crankshaft 32 is rotated, its rotational motion is converted into reciprocating motion and transmitted to the slider 16.

[0076] Thus, by employing a mechanism that converts the rotational motion of the crankshaft into reciprocating motion using a yoke (anti-rotation yoke mechanism), multiple points of force can be connected to a single yoke. Consequently, multiple points of force can be arranged in a direction orthogonal to the axial direction of the crankshaft (a direction orthogonal to the length direction of the slider).

[0077] Furthermore, by employing a mechanism that converts motion into reciprocating motion using a yoke, the length of the connection between the yoke and the point of application can be shortened compared to mechanisms using links. That is, since there is no tilting effect based on the link ratio, as is present in mechanisms using links, the length of the connection between the yoke and the point of application can be shortened. This allows for a more compact vertical dimension. Additionally, it also reduces the moment of inertia of the drive system.

[0078] like Figure 4 as well as Figure 7 As shown, the drive unit 36 ​​has two main gears 52A and 52B, and has a structure in which each main gear 52A and 52B is driven by two motors 54A1, 54A2, 54B1, and 54B2 respectively.

[0079] The two main gears 52A and 52B have identical structures and are integrally mounted on the crankshaft 32. By using the two main gears 52A and 52B to drive one crankshaft 32, the transmitted torque of each main gear can be reduced. This allows for a reduction in the tooth width of the main gears 52A and 52B, thus reducing their moments of inertia. Furthermore, by using two motors 54A1, 54A2, 54B1, and 54B2 to drive each main gear 52A and 52B respectively, the transmitted torque at each meshing point of the gears can be reduced. This further reduces the tooth width of the main gears, further reducing their moments of inertia.

[0080] Each motor 54A1, 54A2, 54B1, and 54B2 is a servo motor with the same structure. Each motor 54A1, 54A2, 54B1, and 54B2 is mounted on the motor mounting portions 24A and 24B of the crown 24 and positioned in a predetermined location. The output shafts of each motor 54A1, 54A2, 54B1, and 54B2 mounted on the motor mounting portions 24A and 24B are arranged along the axial direction of the crankshaft 32. As a result, each motor 54A1, 54A2, 54B1, and 54B2 is arranged along the length direction of the slider 16. Therefore, even when using motors with larger axial dimensions, they can be compactly mounted. That is, although when the motor is arranged in a direction orthogonal to the length direction of the slider 16, there is a possibility that the motor may extend in the front-rear direction of the frame 12, by arranging it along the length direction of the slider 16, the motor can be housed within the frame 12.

[0081] Pinion gears 56A1, 56A2, 56B1, and 56B2 are mounted on the output shafts of each motor 54A1, 54A2, 54B1, and 54B2. Pinion gears 56A1 and 56A2 mesh with the main gear 52A. Additionally, pinion gears 56B1 and 56B2 mesh with the main gear 52B. Therefore, when each motor 54A1, 54A2, 54B1, and 54B2 is driven, its rotation is transmitted to the main gears 52A and 52B via the pinion gears 56A1, 56A2, 56B1, and 56B2, causing the main gears 52A and 52B to rotate. Furthermore, the rotation of the main gears 52A and 52B causes the crankshaft 32 to rotate.

[0082] The drive of each motor 54A1, 54A2, 54B1, and 54B2 is controlled by the control unit 60. The control unit 60 is, for example, a microcomputer equipped with a processor and memory. In this case, the microcomputer functions as the control unit 60 by executing a prescribed control program.

[0083] [Stamping action]

[0084] When the crankshaft 32 is rotated by the drive motors 54A1, 54A2, 54B1, and 54B2 as described above, the rotational motion of the crankshaft 32 is converted into reciprocating motion by the yokes 34A and 34B, and the slider 16 moves reciprocally in the up-down direction.

[0085] Figure 8 This is a diagram showing the change in the state of the slider when the crank is rotated one revolution. In this diagram, the rotation angle θ of the crankshaft 32 when the slider 16 is at top dead center is set to 0°.

[0086] Figure 8 (A) shows the state of slider 16 when the rotation angle θ of crankshaft 32 is 0 degrees. Figure 8 (B) shows the state of slider 16 when the rotation angle θ of crankshaft 32 is 90 degrees. Figure 8 (C) shows the state of slider 16 when the rotation angle θ of crankshaft 32 is 180 degrees. Figure 8 (D) shows the state of slider 16 when the rotation angle θ of crankshaft 32 is 270 degrees.

[0087] like Figure 8 As shown in (A) to (D), by rotating the crankshaft 32, the crank pins 32A and 32B are eccentrically rotated about the crankshaft 32. Furthermore, the eccentric rotation of the crank pins 32A and 32B causes the bearing portions 48A and 48B fitted to the crank pins 32A and 32B to move along guide rails 46A and 46B within the openings 42A and 42B of the yoke bodies 40A and 40B. As a result, the yokes 34A and 34B reciprocate in the vertical direction. Moreover, the reciprocating movement of the yokes 34A and 34B causes the slider 16 to reciprocate in the vertical direction.

[0088] like Figure 8 (A) Figure 8 As shown in (C), the slider 16 descends within a range of 0° to 180° of the rotation angle θ of the crankshaft 32. Moreover, after reaching the bottom dead center at the 180° position, it turns upward and returns to its original position, i.e., the top dead center, at the 360° (0°) position.

[0089] By continuously rotating the crankshaft 32 at a certain speed, the slider 16 is made to periodically reciprocate in the up-down direction.

[0090] As explained above, the stamping machine 10 according to this embodiment can move the slider 16 using a single crankshaft 32. Therefore, even when pressure is applied to the slider 16 by arranging multiple points of force in the length direction and in directions orthogonal to the length direction, the structure of the drive mechanism for the slider 16 can be simplified.

[0091] Furthermore, by employing an anti-rotation yoke mechanism as the driving mechanism for the slider 16, the length of the connection portion between the yokes 34A and 34B and the force application points 30A to 30D can be shortened. This allows for a more compact vertical dimension of the driving mechanism for the slider 16. Additionally, this also reduces the moment of inertia of the driving system.

[0092] It should be noted that in this embodiment, two main gears drive one crankshaft, but it can also be configured to use only one main gear for driving. By using multiple main gears to drive one crankshaft, the transmitted torque of each main gear can be reduced. This allows for a reduction in the tooth width of the main gears and a reduction in the moment of inertia of each main gear.

[0093] It should be noted that when multiple master gears drive the crankshaft, it is also possible to separately configure multiple crankshafts. In this case, as long as the multiple separate crankshafts are configured on the same axis, they can be regarded as a single crankshaft.

[0094] Furthermore, in this embodiment, two motors drive one main gear, but it is also possible to configure a structure that uses only one motor for driving. As with the stamping machine 10 of this embodiment, by using multiple motors to drive one main gear, the transmitted torque at each meshing part of the gears can be reduced. This allows for a reduction in the tooth width of each main gear and a reduction in the moment of inertia of the main gear.

[0095] Second Implementation Method

[0096] In the above embodiment, a structure in which pressure is applied to the slider at four points has been described. However, according to the present invention, a structure in which pressure is applied at more points can also be realized. Hereinafter, the case in which pressure is applied to the slider at five points will be described.

[0097] Figure 9 , Figure 10 These are partial sectional views of the front and side sides of an embodiment of a stamping machine that applies pressure to the slider at five points. Additionally, Figure 11 yes Figure 9 as well as Figure 10 The diagram shows a top view of the slide block of the stamping machine.

[0098] In the stamping machine 10 of this embodiment, five force application points 30A to 30E are provided at five positions on the upper surface of the slider 16. The five force application points 30A to 30E are arranged at the four corners and the center of the upper surface of the slider 16. Force application point 30A is designated as the first force application point 30A, force application point 30B as the second force application point 30B, force application point 30C as the third force application point 30C, force application point 30D as the fourth force application point 30D, and force application point 30E as the fifth force application point 30E, thereby distinguishing each force application point 30A to 30E.

[0099] By adding a force point at the center outside the four corners, even if the rigidity of the slider 16 decreases, the deflection of the slider when subjected to a concentrated load at the center of the slider can be minimized. This results in a more compact vertical dimension (height) of the slider 16. Consequently, the moment of inertia can be reduced. Furthermore, the overall height of the stamping machine can also be reduced.

[0100] Figure 12 This is a front sectional view showing the outline structure of the slider drive mechanism. Figure 13 yes Figure 12 Sectional view 13-13.

[0101] Except for the fact that it also has a mechanism for applying pressure to the central force point (fifth force point 30E) of the slider 16, the structure is the same as that of the slider drive mechanism 18 of the stamping machine 10 of the first embodiment described above. Therefore, only the differences from the slider drive mechanism 18 of the stamping machine 10 of the first embodiment will be described here.

[0102] like Figure 12 As shown, the slider drive mechanism 18 in this embodiment has three yokes 34A to 34C. Hereinafter, as needed, yoke 34A is designated as the first yoke 34A, yoke 34B as the second yoke 34B, and yoke 34C as the third yoke 34C, thereby distinguishing each yoke 34A to 34C.

[0103] The structures of the first yoke 34A and the second yoke 34B are the same as those of the first yoke 34A and the second yoke 34B of the stamping machine 10 of the first embodiment described above. The first yoke 34A is connected to the crankshaft 32 by means of a crank pin 32A fitting into the opening 50A of the bearing portion 48A provided in the opening 42A of its yoke body 40A. In addition, the first yoke 34A is connected to the slider 16 by means of two connecting portions 44A1 and 44A2 extending from its yoke body 40A, which are connected to the first force point 30A and the second force point 30B of the slider 16. The second yoke 34B is connected to the crankshaft 32 by means of a crank pin 32B fitting into the opening 50B of the bearing portion 48B provided in the opening 42B of the yoke body 40B. In addition, the second yoke 34B is connected to the third force point 30C and the fourth force point 30D of the slider 16 by two connecting parts 44B1 and 44B2 extending from the yoke body 40B.

[0104] The third yoke 34C is connected to the fifth force point 30E located at the center of the slider 16. The third yoke 34C has: a yoke body 40C; a connecting portion 44C extending from the yoke body 40C; a guide rail 46C provided in the opening 42C of the yoke body 40C; and a bearing portion 48C that slides along the guide rail 46C within the opening 42C of the yoke body 40C.

[0105] In addition to the first crank pin 32A and the second crank pin 32B, the crankshaft 32 also has a third crank pin 32C. The third crank pin 32C is located at the center of the axial direction.

[0106] The third yoke 34C is positioned at the location of the third crank pin 32C. The third yoke 34C is connected to the crankshaft 32 by fitting the third crank pin 32C into the opening 50C of the bearing portion 48C provided in the yoke body 40C.

[0107] The structure of the drive unit 36 ​​is the same as that of the stamping machine 10 in the first embodiment described above. That is, it has the following structure: the crankshaft 32 has two main gears 52A and 52B, and each main gear 52A and 52B is driven by two motors 54A1, 54A2, 54B1, and 54B2 respectively.

[0108] According to the above structure, when the drive motors 54A1, 54A2, 54B1, and 54B2 are driven, the crankshaft 32 rotates, and the rotational motion of the crankshaft 32 is converted into reciprocating motion by the yokes 34A to 34C, and the slider 16 moves reciprocally in the up and down direction.

[0109] Thus, according to the stamping machine 10 of this embodiment, even when the slider 16 is pressurized at five points, the slider 16 can be moved using a single crankshaft 32.

[0110] It should be noted that in this embodiment, the case of applying pressure to the slider at five points is described as an example, but according to the present invention, it is also possible to realize a structure that applies pressure at more points.

[0111] Furthermore, in this embodiment, when pressure is applied to the slider at five points, the structure is configured to apply pressure to the four corners and the center of the slider 16, but the position (force application point) of applying pressure to the slider 16 is not limited to this. The position of applying pressure can be appropriately set according to the workpiece, etc. In particular, the fifth point (fifth force application point) other than the four corners can also be set at a position offset from the center. For example, it can also be set at a position offset by a predetermined amount from the center of the slider 16 along the axial direction of the crankshaft 32.

[0112] Third Implementation Method

[0113] Here, the operation method of stamping machinery in the case of continuous automatic workpiece processing is explained. For example, in a multi-station press, when continuously and automatically processing workpieces, it is necessary to ensure the workpiece transport time within one cycle. In the past, the required workpiece transport time was ensured by making the stamping stroke length (slide stroke length) sufficiently long.

[0114] However, as the stamping stroke length increases, the crankshaft torque, the gear torque around the drive system, and the necessary torque of the servo motor in servo stamping also increase. As a result, there is a problem of increasing the size of stamping machinery. In addition, there is also a problem of increased moment of inertia of the drive system and reduced acceleration and deceleration performance of the stamping speed.

[0115] Therefore, in the stamping machine of this embodiment, during continuous automatic processing, the slide is kept at the top dead center for a certain period of time in each cycle. By keeping the slide at the top dead center for a certain period of time, the dwell time can be used for workpiece transport. As a result, the stamping stroke length can be minimized as necessary.

[0116] When the height of the processed workpiece is set as H, the gap between the lower end of the workpiece and the upper surface of the lower die required for conveying the processed workpiece is set as h1, and the gap between the upper end of the workpiece and the lower surface of the upper die required for conveying the processed workpiece is set as h2, the minimum necessary stamping stroke length is 2H+h1+h2.

[0117] Figure 14 This is a graph showing the movement of the slider over one cycle. In this graph, the horizontal axis represents time and the rotation angle of the crankshaft, and the vertical axis represents the sliding stroke.

[0118] Slider 16 is at top dead center at time T0. By rotating crankshaft 32, slider 16 descends and reaches bottom dead center at time T1. At this time, the rotation angle θ of crankshaft 32 is 180°. Then, by further rotating crankshaft 32, slider 16 rises and reaches top dead center at time T2. At this time, the rotation angle θ of crankshaft 32 is 0° (360°). After this, rotation of crankshaft 32 stops, and movement of slider 16 stops until time T3. That is, it remains at top dead center.

[0119] The control unit 60 controls the drive unit 36 ​​by having the slider 16 operate in the aforementioned cycle. That is, the drive of motors 54A1, 54A2, 54B1, and 54B2 is controlled by having the slider 16 remain at top dead center for a certain period of time. In this case, the above control is achieved by stopping the rotation of the crankshaft 32 at the top dead center of the slider 16 for a certain period of time.

[0120] Thus, according to the stamping machine of this embodiment, by operating the slide 16 to remain at the top dead center for a certain period of time, the workpiece conveying time during continuous automatic processing of the workpiece can be ensured. This allows the stamping stroke length to be minimized. Furthermore, by minimizing the stamping stroke length, the area around the drive system can be made more compact. Additionally, the moment of inertia around the drive system can be reduced.

[0121] It should be noted that in this embodiment, the structure is designed to stop the slider at the top dead center for a certain period of time, but it can also be designed to stop the slider near the top dead center for a certain period of time. The key is to ensure the workpiece conveying time. For example, the objective of this invention can also be achieved by slowing down the rotation of the crankshaft at or near the top dead center.

Claims

1. A press machine, wherein the press machine is provided with: a slide supported so as to be able to move reciprocally; only one crank shaft arranged along the length direction of the slide and having a plurality of eccentric portions; a drive section that rotates the crank shaft; a plurality of rotation-stopping lever yoke mechanisms provided at each of the eccentric portions of the crank shaft and converting the rotational motion of the crank shaft into reciprocating motion, the plurality of rotation-stopping lever yoke mechanisms having a plurality of levers that move reciprocally along the moving direction of the slide by the rotation of the crank shaft; a plurality of contact points that link each of the levers to the slide; and a control section that controls the drive of the drive section, at least one of the levers is linked to the slide via a plurality of the contact points arranged along a direction orthogonal to the axial direction of the crank shaft, the plurality of levers are linked to the slide only via the plurality of contact points, if the height of a processed workpiece is set as H, the gap between the lower end of the workpiece and the upper surface of the lower die required for the transport of the processed workpiece is set as hi, and the gap between the upper end of the workpiece and the lower surface of the upper die required for the transport of the processed workpiece is set as h2, the press stroke length is 2H + hi + h2, the control section controls the drive of the drive section in such a manner that the slide stays at or near the top dead center for a certain time in each cycle, the certain time is the time for transporting the workpiece after press working.

2. The press machine according to claim 1, wherein the crank shaft has the eccentric portions at least at both ends in the axial direction, the levers provided at the eccentric portions at both ends in the axial direction of the crank shaft are linked to both ends in the length direction of the slide via a plurality of the contact points arranged along a direction orthogonal to the axial direction of the crank shaft.

3. The press machine according to claim 2, wherein the crank shaft has the eccentric portions also between the eccentric portions at both ends in the axial direction, the lever provided at the eccentric portion between the eccentric portions at both ends in the axial direction of the crank shaft is linked to the slide via one of the contact points.

4. The press machine according to any one of claims 1 to 3, wherein the drive section is provided with: a main gear provided at the crank shaft; a pinion gear engaged with the main gear; and a motor that rotates the pinion gear.

5. The press machine according to claim 4, wherein a plurality of the pinion gears are engaged with the main gear, and the main gear is driven by a plurality of the motors.

6. The press machine according to claim 4, wherein the main gear is provided at a plurality of positions of the crank shaft.

7. The press machine according to claim 4, wherein the motors are arranged along the axial direction of the crank shaft.

8. The press machine according to any one of claims 1 to 3, wherein the control section performs drive that stops or decelerates the rotation of the crank shaft at or near the top dead center of the slide. ​

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