JPH02299720A - Bending machine for plate - Google Patents

Abstract

PURPOSE:To perform highly exact bending with a small scale machine by providing the 1st driving means using air pressure and the 2nd driving means using an electric servomotor to make an upper and lower die mutually approach and separate. CONSTITUTION:The 2nd driving means, with which the upper die 18 and the lower die 16 are caused to approach rapidly from the state that both dies are separated by comparatively large distance to the relative position where both are comparatively approached, is provided. At the last stage of bending process, the 3rd driving means is provided further to perform bending by coining. The above-mentioned 2nd driving means is provided with the 1st sliding member 26 which is supported so as to be freely slid in a vertical direction on a frame 10 and is provided with engaging means 54, 58 with which the upper die and the lower die are engaged freely. The 1st driving means is provided with a pneumatic cylinder 38 and the 2nd driving means is provided with the electric servomotor 68. Thereby, because the whole configuration of working machine can be miniaturized and the space between the above-mentioned upper die and lower die are exactly controlled, highly exact bending can be done.

Description

[Detailed description of the invention]

[Part I of the Invention] (Industrial Application Field) The present invention relates to a sheet metal bending machine such as a sheet metal bending press. (Prior Art) Generally, the bending process of a plate (A) is performed by a bending press or the like. An example of such a bending press is schematically shown in the perspective view of FIG. Brunos is
It comprises one or two C-shaped frames 10. The frame 10 supports mutually parallel apron members 12 and 14 in a generally vertical plane. One of these apron members, for example the upper apron member 14, is connected to the frame 10.
It is supported by the frame 10 so as to be able to move toward and away from the lower apron member 12 fixed to the frame 10 . In FIG. 1, arrow Z indicates the direction of movement of the upper apron member 14, and this direction 2 will be referred to as the "work direction" hereinafter. The upper and lower apron members 12 and 14 constitute mold support members for a pair of upper and lower molds, such as a die 16 and a bunch 18, each having a V-shaped processing portion. With the above configuration, the plate material inserted between the die 16 and the bunch 18 is bent into the shape of these dies when the die 16 and the bunch 18 are pressed into engagement with each other. By the way, in the conventional bending press, the movement of the movable apron member 14 and the application of pressing force are performed, for example, in the following manner. That is, in a small bending machine with a bending length of about 1 m or less, a pressing force is applied to one point in the bending length direction. In addition, in medium-sized and large-sized bending presses with a bending length longer than the above-mentioned length, for both ends of the movable apron member 14,
A pressing force is applied to the left and right sides. Various mechanisms are possible for applying these pressing forces. For example, the pressing forces are generated by a fluid pressure cylinder or a fluid pressure motor. On the other hand, high-precision bending presses require precise adjustment and control of the spacing between the die and bunch in order to achieve bending angles within strict tolerances, and typically use numerically controlled drive motors. (The tolerance of the bending angle is, for example, 1/60th of a time, ie, about 1 minute). In addition, in the numerical control, the die 16 and the bunch 18
It is necessary to continuously detect the interval between A fluid pressure cylinder or a fluid pressure motor that is suitable as a small drive source capable of generating the high pressing force is not suitable for the high precision bending press described above. That is, in general, the fluid main system servomechanism is not only inaccurate, but also because the fluid temperature in the main fluid system changes depending on the ambient temperature, its performance changes significantly depending on the working day. Furthermore, during operation, a large amount of heat is generated and transmitted to the machine frame, etc., which causes deformation of the frame, further reducing machine precision. For these reasons, the high-precision bending presses generally employ electric servo motors that can perform operations consistently with high precision. The electric servo motor is also very efficient and does not generate as much heat as the hydraulic cylinder/hydraulic motor. The disadvantage of the electric servo motor is that it is larger and more expensive than a hydraulic drive means when the required driving force is constant. A further drawback of the electric servo motor is that it requires an expensive mechanism for transmitting driving force to a movable mold support member such as the upper apron member 14 shown in FIG. (Problems to be Solved by the Invention) In other words, in conventional plate bending machines, when fluid pressure driving means such as a fluid pressure cylinder or a fluid pressure motor is used, it is difficult to perform high precision bending through numerical control. The disadvantage of using an electric servo motor is that the structure becomes large and expensive. The present invention was made in view of such conventional technical problems, and its purpose is to provide a compact and inexpensive sheet bending machine that can perform high-precision bending. It is to be. Another object of the present invention is to provide a high-precision sheet material bending machine that requires a very low output servo motor to perform bending with a predetermined bending driving force in a predetermined time. [Structure of the Invention] (Means for Solving the Problems) A sheet material bending machine of the present invention that achieves the above object is characterized by comprising the following. (Function) In the present invention, the mold and the lower mold are separated by a relatively large distance 1. , t: state, the J-die and the lower die are moved toward and away from the first drive means, such as a hydraulic drive means, so that the load and the overall structure of the machine can be reduced in size. In addition, when the upper and lower molds are relatively close to each other, the m1 spacing between the upper and lower molds is precisely controlled when the sheet material is actually bent. − can be done. (Example) First, the principle on which the present invention is based will be explained based on the example shown in FIG. FIG. 2 C schematically shows an example of three stages A, B, and C in bending Lto plate material. In FIG. 2, the die as the lower mold is designated by the number 16, the punch as the upper mold is designated by the number 18, and the direction of operation is designated by the symbol Z. As will be described in detail later, the present invention was based on the discovery that the movement of a die during bending can be divided into two or three movement stages. In FIG. 2, the approach step of the heavy mold 18 with respect to the r mold 16 is indicated by the symbol A. This approach step A starts from a state in which any bending press is fully or partially opened [1], in which the punch 1.8 is 9 and the die 1 is
Placed on 6! , -located at a height a distance H from the plate material W. Note that this state is essential for first bending and ejecting the plate material. The step A ends at the position where the apex of the bunch 18 comes into contact with the plate W, as shown in the diagram (ζ) on the right column of A row in FIG. 2. Referring again to FIG. This corresponds to a bending step in which the punch and die engage with each other and actually bend the plate 1i held between them.In this bending step, the punch 18
The moving step C is called coining and is performed only in the case of high-precision bending. Coining has the following meaning. In other words, if the bending process is completed in the moving step B, when the plate material is taken out from the bending press, the plate material may elastically open again. The actual bending angle does not match the bending angle planned for the bending press. On the other hand, if the coining process is performed with a pressing force that is 5 times less than the pressing force in step B, or more , the bending part of the plate becomes completely plastic (e.g., complete yield state), and the bending angle planned by the bending press becomes equal to the actual bending angle.In this coining stage, the C1 punch 18 and the die 16 The relative movement distance ML is almost zero, and is hereinafter referred to as "virtual movement." As will be explained in detail below, the movement process A, B and C differ in their movement mode, and the suppressing force and movement distance are different. The moving distance H of the moving stage A is generally more than 10 times the moving distance of the above-mentioned stage B1, and is the largest among the three stages. On the other hand, The pressing force in this stage A is 1, which is extremely small and is at most about the weight of the movable apron member 14 and the punch 18. In the above, the weight of the movable apron member 14 and the punch 18 is adjusted by an appropriate weight member. Also, in J-7, the crusher 1o of the bending press is not deformed by the pressing force. In the above, it is desirable that the movable apron portion 4414 and the bunch 18 be moved as quickly as possible.
It is desirable to be driven by full drive force/stop control; 2. Movement Stage B This movement stage B requires an extremely large pressing force. Moreover, since the plate material changes from an elastic state to a locally yielded state in the bending region, the suppressing force 7 increases rapidly as the bending process progresses.

[After 7 days, the bending angle increases while keeping the pressing force constant. This is the so-called air bending process. Next, when the plate materials i'j on both sides of the top of the bending region become parallel to both sides of the top of the die 16 and bunch 18, the pressing force increases rapidly again. This state is the so-called completely bent state. The movable apron member 14 in this movement stage B
and the total distance traveled by the bunch 18 is determined by two components K and ′
It consists of That is, in the moving step B, the die 16
and the bunch 18 are always in contact with each other via the plate material W, and the effect of the pressing force causes deformation of the frame 12 and the like of the bending press. Therefore, in the movement stage B, the drive mechanism that drives the movable apron member 14 and the bunch 18 has a distance corresponding to the deformation of the frame 10 of the bending press, etc., in addition to the relative distance K between the die 16 and the bunch 18. The apron member 14, bunch 18, etc. must be moved by -. Here, the travel distance generally includes about 5
The distance is on the order of mm to 20 mm, and the elastic deformation distance ' is much smaller than the above distance. As already mentioned, the moving distance in this moving stage B is much smaller than the moving pressure MH in the approach stage. Next, in this movement stage B, the die 16 and the bunch 18
and must be moved accurately relative to each other. Therefore, the die 16 and the bunch 18 are moved under numerical control while detecting the relative movement distance and taking corrections due to the deformation of the frame 10 into consideration. Therefore, if the angle at which the bending process returns to the initial state due to elasticity after bending is given, the numerical control enables accurate air bending to various bending angles. The pressing force in the moving stage C is extremely large, for example, five times or more than the pressing force in the moving stage B. Therefore, the magnitude of the pressing force must be adjusted appropriately depending on the size, thickness, and properties of the plate material so as not to deform the bending region beyond the allowable limit. Also in this moving stage C, the movable apron member 1
4 and the bunch 18 have two components:
It is expressed as Here, the moving distance represents the distance between the die 16 and the bunch 18, and is an extremely small distance of about 0.1 mm to several mm. On the other hand, the moving distance L'
represents the distance at which the frame is deformed and is somewhat larger than said distance. As a result, the total moving distance L+L- is
The moving pressure i! in the moving stage B! llK+ is about the same as -. In this movement stage C, a coining force is applied. Therefore, no movement distance is detected in movement phase C. The second gist of the present invention based on the above discovery is that the two movement stages A and B1 or the three movement stages A, B,
The problem lies in determining two or three mutually different drive devices or motor means in order to execute C. First, a general bending press that does not perform the coining process will be described. In this case, said approach step A
This is performed by a high-speed, low-cost first drive means, such as a pneumatic cylinder, which is of a full-open/stop drive force type. In the movement stage B, the movable apron member and the bunch are moved by an electric servo motor equipped with a predetermined drive mechanism. In a conventional bending press with one servo motor, the maximum speed of the servo motor is set to the relative approach speed of the bunch and die in step A above. This maximum speed is, for example, about 10 times faster than the speed of the movement stage B so as not to significantly lengthen the machining time. On the other hand, as is already known, the servo motor has a constant torque, so when the servo motor performs the bending process in the movement stage B, its rotational speed is 10 times lower than the rotational speed in the movement stage A. Therefore, the driving force is also about one-tenth of the nominal driving force, for example. Furthermore, in the bending press in which two movement stages A and B are performed by one motor as described above, the position and speed of the mold must be accurately controlled in movement stage B, whereas the movement stage A must be controlled accurately. Then, such high-precision control would be completely useless. On the other hand, in the present invention already described, the maximum speed of the servomorph that performs the bending -I- in the movement stage H is the maximum speed in the movement stage B (,: slow correspondence j7, for example, The speed at A is on the order of 1-0 times smaller.Thus, the servomorph for such a moving stage I and B is 10 times smaller than the speed for moving stages A and B. It is sufficient to have a nominal driving force of about 1. Next, a conventional bending process 1. which also performs the coining step C is used.
/Explain the /s. As already mentioned, this bending step C
In , the movable side nib 11 member! 14 and the bunch 18 are comparable to the moving distance K + K'' in the bending stage B, but these moving members 1.
:The applied driving force must be 5 times the driving force in bending stage B and can be applied by two people. In such a case, in a conventional bending machine in which one servomorph performs all bending operations, the servomorph clearly has a driving force of about five times the driving force required to perform bending step B. You must have a good Lj. Such driving is possible if the machining time in bending stage C is sufficiently longer than the machining time in bending stage B (about several seconds). 17. However, it is preferable that the coining process is performed instantaneously. Furthermore, the bending step C
What is required in 1. is not to detect minute movements of the movable mold due to the plasticity of the plate material and the elasticity of the machine. This is to measure the processing force applied during filter processing. In an embodiment of the present invention, a first driving means may be used to perform the approaching movement in the movement stage A, and a second driving means may be used to perform the bending stage B and the coining stage C in 71 rows. However, in order to perform the coining step C, it is desirable to use a third drive means separate from the first and second drive means1. stomach. Referring to FIGS. 3 to 5, the bending press according to the first embodiment of the present invention is provided with a C-shaped frame 1o. One or more C-shaped frames 10 are provided depending on the size of the bending plate. In FIGS. 3 to 5, one of these C-shaped frames is shown as [7]. l. If two or more C-shaped frames 10 are provided, these
0 is arranged in the same manner as 17 shown in FIGS. 3 to 5, and a plurality of drive means to be described later are configured to operate in synchronization with each other. Referring again to FIGS. 3 to 5, in the frame 10,
A die (lower mold) support member 12 and a punch (1-mold) support member 14 are supported, and this mold support portion 4412.14
Each die (lower mold) 16 and punch (upper mold) 1
8 is supported. The plate material W is bent by these upper and lower molds 12 and 14 (FIG. 3). 3 and 4, said working direction is again indicated by the symbol Z
It is indicated by. A lower arm 22 and an upper arm 2 are attached to the C-shaped frame 10.
4 is formed. As best shown in FIG.
A first sliding member 26 is supported at -C. More specifically, the first sliding member 26 is moved along the working direction Z by the guide member 3 ( ) provided on the side arm 24 and the guide member 28 provided on the first sliding member side. The arm 24 is slidably supported on the - side. This first sliding member 26 has a box shape, and a second sliding member is supported inside thereof. More specifically, the second sliding member 32 includes a guide member 36 provided on the first sliding member 26 and a second sliding member 32.
The die 1 is slidably supported by the sliding member 26 along the working direction Z by a guide member 34 provided at the die 1 . As shown in FIGS. 3 to 5, a mold support member 14 for supporting the bunch 18 is fixed to the 21'F'l moving member 32. As shown in FIGS. Referring again to FIGS. 3-5, drive means, such as a dual acting pneumatic or hydraulic actuator 38, are provided between the first sliding member 26 and the second sliding member 32. ing. More specifically, a main body 42 of the actuator 38 is fixed to the first sliding member 26, and its piston rod 42 extends parallel to the working direction Z. A fork-like member 44 is supported at the lower end of the piston rod 42, and a sprocket 46 is rotatably supported on this fork-like member 44. Further, the first sliding member 26 and the second sliding member 32 are provided with rack members 48 and 62 that face each other and mesh with the subrocket 46. Therefore, by operating the actuator 38, the second sliding member 32 is moved up and down with respect to the first sliding member 26. The first sliding member 26 and the second sliding member 32 include
Engagement means for detachably engaging the sliding members 26 and 32 is provided. More specifically, the second sliding member 3
2, a pair of engaging members 54 having sawtooth-like engaging portions extending in the working direction 2 are fixed (FIGS. 4 and 5). On the other hand, an engagement device main body 56 is mounted on the first sliding member 26 so as to be slidable in the horizontal direction.
An engaging member 58 having a saw blade-like engaging portion that can freely mesh with the engaging portion of the engaging member 54 is fixed to 6 . The engagement device body 56 is coupled via a rod member 64 to a piston 62 of a hydraulic or pneumatic actuator 60 provided on the first sliding member. Accordingly, the engagement device body 56 is horizontally reciprocated by the hydraulic or pneumatic actuator 60. The actuator 60 is provided with a spring member 66 for biasing the engagement device main body 56 to the left in FIG. 4. Therefore, the actuator 60
When no fluid is supplied to the engaging member 58 , the engaging portion of the engaging member 58 engages with the engaging portion of the engaging member 54 . The upper arm 24 is provided with a second driving means for moving the first sliding member 26 in the vertical direction. As already mentioned, this second drive means carries out said movement step B. As best shown in FIG.
It consists of: This drive gear 70 transfers the driving force from the numerically controlled electric motor 68 to a driven gear 72 via a toothed belt 74.
Communicate to. The driven gear 72 is fixed to a female threaded member 76 rotatably supported by a bearing portion 78. Note that the bearing member 78 is fixed to the upper frame 24 of the frame 10. A horizontal rod portion 80 extending in a direction perpendicular to the working direction Z is coupled to the female thread member 76 . That is, the horizontal rod member 80 has a ball screw 82 that engages with the female thread member 76. A prismatic member 84 is provided on the opposite side of the horizontal rod member 80 from the ball screw 82. A well-known dripping brake 86 is fixed to this prismatic member 84. The operation of this dripping brake will be explained in detail later. At the tip of the prismatic member 84 (on the right side in FIG. 3), there is a pair of wedge members 88 (
(See Figure 5) is the installation. The upper wedge surface 92 is comprised of a horizontal surface formed in a crosspiece member 94 of the upper arm 24 and cooperates with a corresponding horizontal surface of the wedge member 88. On the other hand, the lower wedge surface 90 is connected to the first sliding member 26.
It is formed on the upper surface, has an inclination corresponding to the lower surface of the wedge member 88, and cooperates with the lower surface of the wedge member. In addition, as shown in FIGS. 3 and 4, the upper and lower wedge surfaces 90° 92 have the following:
A roller is provided to eliminate friction. Referring to FIG. 5, a pair of spring members 42 are provided between the upper arm 24 and the first sliding member 26 to bias the first sliding member 26 upward. These spring members 42 are connected to the first sliding member 26
and second sliding member 32 are configured to support the entire weight of the movable part when engaged with each other. Therefore, the upper and lower wedge surfaces 90 and 92 and the wedge member 88 are reliably engaged. In order to detect the vertical position of the movable mold 18 in the moving stage B, the first sliding member 26 is provided with an optical scale 96 extending in the working direction Z. Meanwhile, the upper arm 24 is provided with an optical-electronic detection device (not shown) that cooperates with the optical scale 96, the output of which is manually applied to the servo motor 68. Thereby, the drive system of the movable mold 18 by the servo motor 68 forms a closed loop. Referring to FIG. 3, in order to perform the coining step C, a die (lower mold) 16 is provided in the lower arm 22 of the frame 10.
A drive means is provided. More specifically, a double acting pneumatic cylinder 98 is fixed to the F-side arm 22. This pneumatic cylinder 9
8 is provided with a horizontal rod member 102 extending in a direction perpendicular to the working direction Z. This horizontal rod member 1
A wedge member 1 having the same structure as the wedge member 88 is attached to the tip of the wedge member 88.
．． 04 is bearing 1. On the other hand, a third sliding member 106 is supported on the lower arm 22 so as to be movable in the working direction Z, and a lower die supporting the die (lower mold) 16 is supported on the third sliding member 106. The mold support member 12 is formed L7. The wedge member 104 includes a lower wedge surface 108 formed on the fixed block member 112 on the lower arm 22 and an upper wedge surface 1 formed on the third sliding member ]-06.
It is designed to collaborate with 10. Note that the earthwork wedge surface 1. ．． 08. 1.1.0 is also provided with rollers to prevent friction on the wedge surface. Referring again to FIGS. 3 to 5, the operation of this embodiment will be explained in 1 to 1. First, in the approach step A, the second sliding member 32 is released from the first sliding part 26, and the movable mold support member 14 is at the height position shown by the two-point line 14a in FIG. rises to. When the plate material W is inserted between the upper and lower molds 16 and the plate 8, the fluid pressure or pneumatic actuator 38 in the first drive means is activated, and the screw rod 42
In the figure, it is lowered in the direction of arrow F]. By the magnification mechanism 46, 48, 52, the second sliding member 52 is lowered by a distance H shown in FIG. The distance H is twice the moving distance of the front piston rod 42 due to the magnification mechanism 46, 48, 521.The movable mold support member 14 is moved as shown in FIG. It is located at the height position indicated by the two-dot chain line 14)3. In this state, the engagement device main body 56 having the engagement member 58 that has been released from the engagement member 54 is driven forward by the pressure drop within the actuator 60. Then, the engaging members 54 and 58 are engaged (7), whereby the first sliding member 26 and the second sliding member 32 are fixed to each other. Here, after numerical control, the bending step is performed. B is started. That is, as shown in FIG. 3, a start signal is given to the numerically controlled electric servo motor 68, and Ij I'll is performed based on a preset program. In this control process, The lowered positions of the movable mold support member 14 and the bunch 18 are detected by the optical scale 96. By the operation of the electric servo motor 68, the wedge member 88 moves in the direction of arrow FB in FIGS. 3 and 4. The mold support member 14 and the bunch 18 are moved to
3 is moved in the direction of arrow F4, and a distance +K'' is carried out in FIG. 2B. Once said bending step B has been completed, the coining step C in FIG. 2C is then carried out. To carry out the coining step, the hydraulic actuator 98 is actuated and its piston 100 and wedge member 104 are moved in the direction of arrow 5. This wedge member 1
04, the third sliding member 106, the lower mold support member 12, and the die 16 are slightly moved in the direction of arrow F6, and are moved by a distance L+L− in FIG. 2C. Note that the coining driving force applied to the wedge member 104 is detected by an electrically controlled pressure regulator 114 connected to the fluid pressure actuator 98 via a pressure change inside the fluid pressure actuator 98. By the way, during the coining process, the bunch 18
The movable members including the mold support member 14, the first sliding member 26, the second sliding member 32, etc. must be prevented from returning upward due to the coining driving force. That is, the speed reduction mechanism composed of the female screw member 76 and the ball screw 82 is generally reversible, and there is a possibility that the movable member returns in the reverse direction. In order to prevent this backward movement, the horizontal rod member 82 is provided with the dripping brake 86. This dripping brake 86 transfers the reaction force caused by the coining process directly from the wedge member 88 to the upper arm 24 of the frame 10.
to communicate. Thereby, there is no possibility that the screw devices 76, 82, which are small compared to the magnitude of the coining driving force, will be adversely affected. In the embodiment, the servo motor 68 includes:
Although the numerically controlled electric servo motors are preferred, hydraulic servo motors may also be used. Furthermore, the third driving means for coining is not necessarily necessary and can be omitted. the first sliding member and the second sliding member in the upper arm 24;
It is also possible to configure the third driving means by providing a third sliding member inside the driving member made of a sliding member and sliding the third sliding member. A second embodiment of the present invention will be described based on FIGS. 6 to 9. Referring to FIGS. 6 and 7, this bending press has a first
A pair of C-shaped support frames 1100 are provided as support frames. A lower apron member 1102 is fixed to the lower arm of this first support frame 11.00, and a die 1104 is fixed to the upper edge of this lower apron member 1102. An upper nib 62 member 1106 is supported on the upper arm of the first support frame 1100 so as to be vertically movable, and a bunch 1108 is fixed to the lower edge of the upper apron member 1106. In the following description, the upper and lower apron members 110
2 and 1106 will be described as being composed of one plate, but it is also possible to physically divide them into units. As shown in FIGS. 6 and 8, the first support frame 1100
A vertically actuatable, dual-acting hydraulic or pneumatic actuator 1112 is mounted on the upper end of the actuator. A bracket 1116 is supported on the operating shaft 1114 of the actuator 1112, and the upper apron member 1106 is suspended from the bracket 1116. The actuators 1112 (left and right in FIG. 6) supported by the first support frame 1100 are operated in synchronization with each other. Therefore, the bunch 1108 is
104 in the same manner over its length, and returns to the initial position in the same manner after bending. When the bunch 1108 approaches the die 1104 to a predetermined distance, the bracket 1] 16
Spring 1 that contacts 18 and is provided below the stopping member.
The downward movement is stopped by the elastic force of 20. In addition, in the above, the spring 120 is attached to the upper apron member 1.
It is pre-biased to support the weight of the movable members including 106 and bunch 1108. Referring again to FIGS. 6 and 7, the bending press is provided with three or more C-shaped second support frames 122 for carrying out the actual bending process. More specifically, each second support frame 122 is statically mounted to a horizontal bin 124 fixed to the lower apron member 1102. Note that the second support frame 12 may be
2 can also be mounted on the lower apron member 1102 so as to be rotatable about the horizontal pin 124. As best shown in FIG. 7, the weight of the second support frame is supported by a spring 126 provided at its rear end. Further, the upper arm of the second support frame 122 is connected to the upper apron member 110 via an appropriate roller 128.
It is biased in contact with the back surface of 6. A reaction device 130 is attached to the upper arm of the second support frame 122.
is supported. This reaction device 130 comprises a hydraulic or pneumatic actuator 138. At the tip of the piston rod 134 of this actuator 138,
A reaction force rod 136 is provided. Incidentally, as will be explained in detail later, the reaction force rod 136
A servo motor device 14o (FIG. 9) is supported on the upper apron member 106 correspondingly. In FIG. 7, the hole 1 for the die 1104 is
．． Said servo motor device 1 at the end of the approach phase of 10 g
The position of 40 is shown by a solid line, and the position of the servo motor device 140 upon return to its initial position is shown by a broken line. More specifically, a spherical gap 142 is provided at one end of the servo motor device 1.40, and a spherical gap 142 is provided at one end of the servo motor device d1. /l, O reaches the final position of the approach stage, the reaction force lot 1'-36 of the reaction force value B 1.30 is applied so that the servo motor device 140 and the upper apron member 1106 do not return upwards. advances to the position shown in FIG. Referring to FIG. 9, the servo motor device 140 includes:
A block 1 provided at a position corresponding to the second support frame 1-22 in the longitudinal direction of the upper edge of the upper apron member 1106
It consists of 44. This block 144 comprises a three-sided wedge 146 equipped with rollers. A vertical guide member 1-50 is also fixedly provided on the upper apron member 1106, and a movable block 1-48 on which the spherical cap 142 is formed is vertically movable downward. Supported. This movable pro-nk 148 has. An inclined wedge surface 152 facing the horizontal wedge surface 146 is formed. A corresponding wedge member 154 is inserted between the lower wedge members 146 and 152. This wedge member 154 is located between the operating shaft and the ball screw 1.
It is fixed to the tip of 56. A female screw member 158 that cooperates with this ball screw 156 is
It is rotatably supported by a bearing 1-60 provided on a support block 162 fixed to two end edges of the upper apron member 1106. The one-way apron member 1106 also supports a numerically controlled electric servo motor 164 that can rotate the dovetail screw member 158 via a transmission device such as a toothed belt. In the configuration, the first drive device 1112.111
Bunch 1 for die 1104 by 4.1116]0
When the approach step 8 is completed, the numerically controlled servo motor 164 provided on the second support frame 122 is activated, and the wedge member 154 is compressed and inserted between the upper and lower wedge surfaces 146 and 152, and the bending step is completed. is executed. The plurality of numerically controlled servo motor devices 140 arranged along the longitudinal direction of the upper and lower molds are substantially all the same. Referring to FIG. 7, the second support frame 1-22 also includes an interval detection device]70 for detecting bacteria between the bunch 1-08 and the die 1-04, and a second support frame during processing. A deformation detecting device 172 for detecting deformation of 122 is provided. More specifically, a lower arm 174 of the distance detection device] 70 is fixed to the lower apron member 1102, and an optical detection sensor that cooperates with a suitable optical scale 180 is attached to an upper arm 176 that is continuous with the lower arm. Supported. -7. The lower arm 180 of the deformation detection device 172 is fixed to the lower arm of the second support frame 122, and the gravity arm 1-82 connected to the lower arm is connected to the deformation of the second support frame 122. A detection sensor for detecting is supported. Therefore, the bunch 1108 and the die 110
It is possible to determine the origin position in the state in which 4 and 4 are engaged. This makes it possible to control the second support frame 122 and the upper apron member ii02. As already explained, since the apron member of this embodiment is composed of a continuous integral member, the deformation detection device is necessary. The present invention is not limited to the above-described embodiments, but may be implemented in other embodiments as understood from the claims. For example, in the first and second embodiments, the upper apron It is also possible to adopt a structure in which the lower apron member is supported by the support frame so as to be movable up and down, and the die approaches and leaves the bunch. According to the plate bending machine, since the first drive means and the second drive means are provided to move the upper and lower molds toward and away from each other, it is possible to perform high-precision bending despite being small and inexpensive. can.

[Brief explanation of the drawing]

Figure 1 is an explanatory diagram showing the general configuration of a bending press, Figure 2
3 is a cross-sectional view of the first embodiment of the invention, FIG. 4 is a partially enlarged view of the portion indicated by arrow IV in FIG. 3, and FIG. The figure is a sectional view taken along the line V-V in FIG. 4, FIG. 6 is a plan view of the second embodiment of the present invention, FIG. FIG. 6 is a partial sectional view taken along arrow VIII in FIG. 6, and FIG. 9 is a partial cross-sectional view of the second
FIG. 3 is a front view of the embodiment. frame,
,,10 upper molds (bunch) ,,1
8 Lower mold (Die), 16 Fluid or pneumatic actuator, 38 Numerically controlled electric servo motor, 68 Fluid pressure actuator, 98 Fig. 3 Fig. 4 Fig. 7 Fig. 8

Claims (14)

[Claims] (1) A frame; an upper mold and a lower mold that are provided on the frame so as to be able to approach and separate from each other, and that are capable of bending a plate material inserted therebetween; the upper mold and/or Alternatively, a plate bending machine comprising: a second driving means for quickly bringing the lower die close to each other from a relative position where the two dies are relatively widely separated to a relative position where the two dies are relatively close to each other. (2) Claim 1 further comprising a third drive means for performing coining bending in the final stage of the bending process.
The plate bending machine described in . (3) The second driving means includes a first sliding member supported by the frame so as to be slidable in the vertical direction, and
The sheet material bending machine according to claim 1, further comprising engagement means (54, 58) for releasably engaging the upper die or the lower die. (4) The plate bending machine according to claim 3, wherein the first driving means is supported by the first sliding member. (5) The plate bending machine according to claim 1, wherein the first drive means includes a pneumatic cylinder, and the second drive means includes an electric servo motor. (6) The second drive means includes a first drive means that is slidable in the vertical direction.
The sheet material bending machine according to claim 5, further comprising a sliding member and a wedge member capable of moving forward and backward by rotation of the electric servo motor to push down the sliding member. . (7) The plate bending machine according to claim 7, wherein the second driving means includes a brake means for preventing the wedge member from moving forward or backward. (8) The engagement means includes a first engagement member (54) provided on a mold support member (14) that supports the upper mold or the lower mold, and the first sliding member (26). The sheet material bending machine according to claim 4, further comprising a second engaging member (58) which is provided to be movable in the horizontal direction and can be freely engaged with and disengaged from the first engaging member. (9) The mold support member (14) comprises a second sliding member (32) slidably supported by the first sliding member. Plate bending machine. (10) The first driving means includes a first rack member fixed to the first sliding member, and a second rack member fixed to the second sliding member in a manner facing the first rack member. a sprocket member rotatably provided at the tip of a piston rod of a fluid pressure cylinder fixed to the first sliding member and meshing with the first rack member and the second rack member; The sheet material bending machine according to claim 9. (11) The third driving means includes a third sliding member (106) supported by the frame so as to be slidable in the vertical direction;
3. The plate bending machine according to claim 2, comprising: a fluid pressure cylinder; and a wedge member provided at the tip of a piston rod in the fluid pressure cylinder to move the third sliding member up and down. . (12) The second driving means includes a first sliding member that is slidably provided in the vertical direction with respect to the frame, and a wedge member that drives the first sliding member, The driving means is fixedly provided to the upper mold or the lower mold,
a fluid pressure cylinder that is mounted on the first sliding member so as to be slidable in the vertical direction on the first sliding member and that moves the second sliding member with respect to the first sliding member; 2. The plate bending machine according to claim 1, wherein the first sliding member is provided with fixing means that can be fixed to the second sliding member with respect to the first sliding member. (13) A frame, upper and lower molds that are provided on the frame so as to be able to move toward and away from each other and are capable of bending a plate material inserted between them, and are supported on the frame so as to be slidable in the vertical direction. a wedge member for moving the first sliding member upward or downward; a second sliding member that fixedly supports the mold; a pneumatic cylinder that is supported by the first sliding member and moves the second sliding member up and down with respect to the first sliding member; and the first sliding member. A plate bending machine comprising: a fixing member provided on a moving member and capable of fixing the second sliding member to the first sliding member. (14) The upper mold and/or the lower mold are quickly moved from a relatively large relative position to a relatively close relative position with a relatively small force, and the upper and lower molds are mutually connected via the plate material. When it comes into contact with the mold, under numerical control, the upper and lower molds are brought closer together to perform air bending at a precise angle.After the air bending is completed, except for the bending of the bending tip, coining is performed with a large force. A sheet material bending method characterized by: