KR960007488B1 - Sheet metal bending device - Google Patents

Abstract

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Description

Plate bending device

1 is a schematic overall configuration in which the sheet bending apparatus is in an at-rest position according to the present invention.

FIG. 2 is an enlarged partial sectional view showing a part of the bending tool region of the present bending device in the operating position as compared to FIG.

3 is a cross-sectional view showing the main components of the bending device according to FIGS. 1 and 2;

4 is an exploded perspective view showing a pair of tool parts including a hinge connection used for bending punches of the bending device according to FIGS. 1 to 3;

5, 6 and 7 are partial cross-sectional views showing the bending state of the bending tool and the plate formed at various bending stages.

FIG. 8 is a cross-sectional view of any one of the bending punches modified in the embodiment shown in FIGS. 1 to 7 and mounted to the bending device shown in FIGS.

9 is a cross-sectional view of an embodiment partially modified from the embodiment shown in FIG.

10 is a schematic configuration diagram showing a bending tool configuration of a more modified bending device.

11, 12, 13, 5, 6 and 7 are cross-sectional views showing the various stages of the plate bent by the bending apparatus according to FIG. 1, FIG. 11 shows the starting position,

12 shows the intermediate position,

13 shows the end position.

* Explanation of symbols for main parts of the drawings

2: lower frame 5: vertical guide

9: Tool support 10: Counter punch

14; Spindle Drive 17: Spindle Nut

19,20: bending punch 22: bending corner

27,28: shaft 53: hinge connection

54: hinge pin 55: tool segment

61,52: Tooth rail 63,64: Pinion

74: transverse beam 75: bearing member

78: sliding groove 82: protrusion

85: tool insert

The present invention has three punches, two adjacently arranged, rotatably connected bending punches, the bending punches forming a plate support plane having a sheet contact area in the stop gear, and also the bending Having a counterpunch located opposite the punch, the counterpunch is linearly movable between an operating position and a retracted position in the plate, two punches rotatably mounted to the pivoting drive, each connected thereto, The sheet material relates to a sheet bending apparatus that is bent by at least one of the bending punches centered on a counter punch at an angled position.

In general, the most well known metal sheet bending or folding technique involves moving an upper bending punch to a plate seated on a lower die, which presses the sheet into the die at the point where the bending edge is formed. Bending the sheet (see FR-A-2 201 973 and US-A-2649 128).

In this process, the bending edges typically cannot be formed precisely and precisely, and each die can only be operated with a limited bending, ie a very specific bending angle, It is very disadvantageous that a significant amount of energy applied for the sake is lost by friction on the die.

These disadvantageous problems basically also apply to die devices in which the die is divided into two parts, mounted movably on one support, and in particular rotatably connected relative to one another.

In this context, for example, DE-C-115 961 or EP-A-379 886, FR-A-1 221 933 and DE-A-1-402 118, DE-A-2 418 669, US-A -1 045 089, US-A-1 258 892, US-A-1 633 744, US-A-2 433 841, JP-A-62-127 125, JP-A-63-36923 and JP-A- 63-199028. In all these structures, the actual bending work is done by the upper bending punch, so that the punch must be made very robust, and accordingly a large weight actuator must be fitted.

The bending device used for profiled sheets is already known (WO 81/02535), which is used to form corrugation, wherein the upper and lower movable upper punches are fixed lower punches and both sides thereof. It is located at each and cooperates with obliqueauxiliary punches that can be moved up and down in the direction of the principal plane in an inclined state. The upper punch forms a corrugation on the plate with the fixed lower punch facing it, and the two side slanted punches form the corrugation in the following order. Known bending apparatuses are not designed or simply not suitable for simply bending a sheet so that the bending edge is as sharp and accurate as possible.

There is also a manual rotary bending device in which the bending plate is clamped between a fixed lower web and an upper web joinable thereto, and the bending operation is performed by one rotatable lower bending punch. Presented. In addition, US-A-3 044 526 or DE-A-1 402 838, the sheet bending apparatus shown in US-A-3 282 976, GB-A-1 119 811 and GM-A-2 050 887, respectively, It has also been proposed a structure in which two lower bend punch structures are rotated about a horizontal axis in opposite directions to bend the plate to be bent around the upper counterpunch.

The pivot bearings used for the two lower bend punches are mounted on the outside on two end faces of the bending device, and a pivot drive device in the form of an actuating cylinder is provided on this end face. These bending punches must consist of a structure of quite large weight, in particular a large width (2m or 3m) of the device is required, the exact bend cannot be obtained in the central region of the device, as well as usually in the central region. The sheet material is disadvantageous in that it is bent to have a much more open shape than in the end region, that is, to have one bent shape along the longitudinal direction of the bend.

In general, an excessively large structure of a bending punch is accompanied by a limited width of the device because of its heavy weight, which means that the width of the device exceeding 3m is not appropriate because the total weight of the device is excessively increased. This large structure results in the weight of the bending device being up to 15 tons and up to 20 tons.

It is an object of the present invention to form a sharp and accurate bending edge even when consuming a relatively small amount of energy in bending operation of a plate, in particular, various bending surfaces are obtained by a plurality of bending operations, and have a simple structure as much as possible. The structure of the punch and frame is significantly less than that required in the prior art, and therefore, to provide a bending device of the first defined manner that can reduce the weight by a considerable amount. In addition, it is possible to treat the plate as carefully as possible during the bending operation.

According to the present invention, a sheet bending apparatus of the first defined method is provided in which the two bending punches are opposed to each other along each corner at a stop position, and over the full width of the bending apparatus by a hinge connection offset from the sheet support plane. Directly connected to each other, a depression is provided between the plate contact area and the hinge connection of each bending punch, and the bending punches are detachable tool members disposed adjacent over the entire width of the bending device. segments) are mounted, and the supply members are connected to each other in pairs by hinge connecting members, and the hinge connecting portions of the bending device are formed by the hinge connecting portions of all pairs of tool members.

Accordingly, the bending device of the present invention has an articulated connection formed in two bending punches in an operating region and a power flux provided through the hinge connection during the bending process of the sheet, thereby providing the inside of the hinge. At least partially balanced in the horizontal component of the forces exerted during the bending process at, which is essentially done directly in the operating area, which on the other hand avoids the installation of excessive pivot bearings at the end faces of the bending punch. On the other hand, it is possible to limit the excessive size of the bending punch itself. Various experiments have proven that the same performance can be obtained in the bending apparatus of the present invention, for example, compared to a 15 ton bending apparatus. A reduction effect of / 5 to 1/10 is obtained.

By deviating the hinge connection from the plate support plane and providing a recess in the bending punch, a smooth and smooth bending operation of the plate during bending operation and optimum action force conversion in the initial stage of bending are obtained. In addition, by mounting the tool members connected to each other in pairs to the bending punches, it is possible to quickly switch the bending device, in particular, it is possible to work with different widths.

In terms of weight reduction, it is particularly advantageous if several pivoting drives engage each of the two independently rotatable bending punches over the full width of the bending device, and the counter punch is only linearly movable.

In a plurality of bending operations, a phenomenon in which the bent plate strikes the counter punch already bent portion (so-called collision phenomenon) may occur during the second or third bending process. This is for example the counter punch can be avoided and eliminated by pivoting. However, in order to perform this, the rotary mounting structure of the counter punch is required, and the pivot bearing and the punch itself should be appropriately applied with counter-force to the batch door plate bending work. Thus, what is preferably to be selected and provided is a simple linear actuation of the counter punch, although not absolutely necessary, providing the possibility of bending plate material being avoided, and also in the case of the collision described above, the counter punch It is particularly advantageous if the two punches are connected to independent pivoting devices in order to enable bending after striking.

By means of an independent pivot drive, the plate is held on the side of the bending punch in which the side of the plate including the plate portion already bent is positioned by simply stopping one bending punch in the event of a collision, and the other side of the bending punch It is possible to further rotate to bend the plate. In addition, by the asymmetrical mode of operation, at least the majority of the horizontal component of the bending force is compensated through the hinge connection so that only relatively small forces are induced into the bending punch and from there into the frame.

An embodiment which is dynamically identical to the embodiment described above is preferred in some cases with regard to the fixing part structure of the bending device (for example, when considering a fixed mounting structure of one plate part during bending operation), and also during bending punches. Either of which is fixedly mounted, the other is rotatably mounted like a counter punch, and the rotatable bending punch is characterized in that it can be driven at twice the speed with respect to the angular velocity of the counter punch.

In general, the bending device is particularly suitable for the complete folding operation due to the articulated connection, which is particularly advantageous in that the counter punch is designed to be separated and retracted from the plate in order to fold it in the final bending stage of the plate. .

Due to the hinged connection of the bending punch according to the invention, the present bending device has a simple plug-in connection to the side facing the plate contact area on the bending punch that acts as a tool support in a more advantageous manner, i. It is possible to mount the tool member as a tongue-and-groove connection means.

And, in order to facilitate the assembly and replacement of the tool members, it is more advantageous to provide the tool member pairs with hinge pins corresponding to the lengths of the members. The hinge pins are more advantageous if they each protrude into the hinge holes of the pair of adjacent tool members on one side.

When exchanging tools, all of the hinged pins arranged in a line can be displaced linearly by, for example, a linear amount of protrusion relative to each of the adjacent members in common, so that the respective members can no longer be supported by each other.

On the other hand, for stability reasons, it may be desirable to provide one common through hinge pin that extends through all these tool members.

In order to facilitate the replacement work taking into account the wear occurring during operation, it is also desirable to provide separate inserts for forming a plate contact area in the tool member.

These inserts are screwable to the tool member respectively.

Particularly beneficial and effective drives are connected by a pinion rigidly connected to the combined bending punch and mounted on a shaft, and on a circular arc-shaped toothed rail, each provided as a pivot drive. Obtained by It is further advantageous if the toothed rail is mounted in an arcuate bearing, ie in the bearing recess of the stationary bearing part. In this way, each bending punch can be mounted on the frame of the bending device at the same time via the tooth rail. It is also desirable to provide two separate bending motors to rotatably drive the two axes coupled to the bending punch.

Hereinafter, the present invention will be described in more detail with reference to the drawings.

According to FIG. 1, a preferred instantaneous sheet bending device, a bending device or a bending press according to the present invention is denoted by reference numeral 1 and is provided with a lower frame 2 and a vertical guide 5 thereon. Is formed on the major end support (3) (4), and in the vertical guide (5) a web (Web) or blade type counter punch (10) (also called an upper tool or simply a blade) The upper tool support (9) comprising a guide is configured to be vertically movable up and down. Preferably, the counter punch 10 is detachably fixed to the tool support 9 and can also be integrally fixed and has a shape such as a cutting edge, but differs depending on the type of bending material to be produced. A lower bend edge 13 is provided, which may have a cross section in shape (see also FIG. 3).

In order to raise and lower the upper counter punch 10, a conventional spindle drive is used, which is indicated by reference numeral 14 in FIG. This spindle drive 14 is equipped with a spindle 16 driven by, for example, an electric drive motor, and if necessary a gear and clutch (not shown) can be used and a spindle nut connected to the tool support 9. In cooperation with (17), the tool support (9) is moved up and down during the rotation operation of the spindle on the guide (5) together with the counter punch (10). These spindle drives 14 and other drive means are attached to the frame 2 in a conventional manner as described.

Then, two lower plates or web type bending punches 19 and 20 are provided to bend the plate 18 (see FIGS. 5 to 7).

These two lower bending punches 19 and 20 are rotatably mounted on the frame 2 and located in the region of the bending edge 22 formed on the plate 18 to be bent, as will be described later. Rotatable about a common pivot axis 22 (see FIGS. 5 to 7), which is formed by the guides 5 and 6 directly below the bent plate 18. The counter punch 10 is positioned in the up and down moving plane 23.

The driving device for rotating the lower bending punches 19 and 20 on the common rotary shaft 21 is a rotary driving device, and in a typical embodiment, a plurality of rack and pinion gears (first To 24 in FIGS. 3 to 3, which are formed along the width of the bending device 1. In more detail, each arc-shaped rack gear or geared rails 61 and 62 is mounted in the lower region of each lower bending punch 19 and 20, as well as in the first to third views. 8 and 9 degrees are clearly shown.

The racks or parts 61 and 62 on which such gears are formed are wheels 63 having gears parallel to each other and respectively placed on shafts 27 and 28 parallel to the bending punches 19 and 20 ( 64) is engaged with the engagement. Each of these two shafts 27, 28 is driven by, for example, electric drive motors 72, 72, as shown in FIG. 1, and may optionally be drive-connected through a gear (not shown). connect.

The two shafts 27, 28 extend over the full width of the bending device 1 and are fitted by suitable bearing members 75, as will be described in more detail below, and rotate on the frame 2. Possibly journaled and positioned on the midpoint and end face within the area of each rack and pinion gear 24. For each of the recreational gears 24, gear racks 61 and 62 are provided and rotated, as are the gear wheels 63 and 64 mounted on the respective shafts 27 and 28, and have already been rotated above. As pointed out, some of the rack and pinion gears 24 may be uniformly positioned over the width of the bending device 1 as the cladding drive means to provide a uniform drive torque. Accordingly, the gear racks 61 and 62 together with the rotating shafts 27 and 28 are moved along an arc-shaped passage whose center is located on the pivot shaft 21, and FIG. 5 (inactive position) And the lower bending punches 19 and 20 connected thereto as shown in detail in FIGS. 6 and 7 (rotating separation operation position) to rotate to separate each other.

Several bearing members 75 extending transversely to the fixed transverse beam 74 of the frame 2 are mounted on the transverse ratio 74 in the position of the rack and pinion gear 24, which on the one hand In order to mount the shafts 27 and 28, on the other hand, the bending punches 19 and 20 are positioned over the entire width of the bending device for mounting on the frame 2 as indicated above.

The bearing member 75 comprises a bearing 77 exchangeable via a bearing cover 76 (see FIGS. 2 and 3) releasable for the shafts 27 and 28, on the other hand An arc-shaped sliding groove 78 is provided on both sides of the region (right side of FIG. 2), and in the groove, a guide key in which the arc-shaped gear rack or the gear members 61 and 62 are curved in such a matching shape or Guides 79 are slidably movable by means of ledges 79. Thus, two gear members 61 and 62 are each slide guided on the bearing member 75, one of which is used for the shaft 27 and the other for the shaft 28.

The load is controlled by the bearing arrangement with the gear racks 61 and 62, guide keys 79, arcuate sliding grooves 78 and bearing members 75 of a relatively rigid configuration. The acting force absorbed through the width and generated during the bending operation is guided to the frame 2 and the transverse beam 74 in a uniform distribution manner. Therefore, the configuration of the bearing member 75 of relatively small size is possible.

In FIG. 3 a pinion 63 connected to the shaft 27 is shown, which is located in front of the bearing member 75 shown in FIGS. 1 and 2 and connected to the shaft 28. 64 is located at the rear side of the bearing member 75 as shown by the dotted line in FIG. On the other hand, the bearing 77 used for the shaft 78 is replaceable through the bearing cover 78, and is shown in FIG. 3 as shown in the shaft 28 located on the right side in FIG. In addition, in FIG. 3, the two shafts 27 and 28 have a cross-section in the form of a so-called lobed cylinder, so that the pinions 63 and 64 can be rotatably mounted without weakening the cross section. For example, it is similar to a key-key way connection. Each of the bending punches 19, 20 connected to the accessory gear members 61, 62 is each gear member 61, 62, for example as shown in FIGS. 8 and 9 and 3. It may be accommodated in a simple plug-on seat or a press-in seat method between the seating protrusions 80 and 81 formed integrally with each other. However, it may be screwed on the one hand.

It can be seen from FIGS. 2 and 3 that the two bend punches 19 and 20 are arcuately connected by hinged connecting members over their entire operating width along their upper inner edges. According to FIG. 4, a plurality of hinge holes 52 are shown extending through the hinge pins 54 in a combined state. The hinge connecting device 53 is provided with a hinge pin 54, the two bending punches (19) 20 to form the above-mentioned front shaft 21, the rotational operation around it.

More specifically, the bending punches 19 and 20 are designed as tool-holders with a detachable and replaceable tool member 55 alone, the tool members 55 being hinge pins 54. Pairs are connected in the longitudinal direction by).

The tool member 55 is held in the bending punches 19 and 20 to a plug-in connection of a simple structure having a longitudinal protrusion 82 and a support recess 83. By acting as a tool support, the tool member 55 can be exchanged particularly simply and quickly. On the other hand, it has been found that no fixed coupling means is required between each tool member 55 and each tool support or bending punch 19, 20, which means that the horizontal component of the action force during bending during actual operation is Plugs in which at least the force in the vertical direction or the force acting in the plane of the bending punches 19, 20, at least compensated by the hinge connection 53, is easily made by the protrusions-and the grooved connections 82, 83. It is delivered by an in-connect (protrusions 82, grooves 83). Considering the wear that occurs during actual operation, it is appropriate to provide a tool insert 85 which imparts suitable bending operation to the plate through the contact area 84 (see FIGS. 3 and 4 and 8). Insertion stand 85 is made of a rigid metal insertion member and is screwed by bolts 86 to tool member 55 or bending punches 19 and 20, respectively (see FIG. 8). The structure of the modified insert is additionally shown in FIG. 9 with a protrusion for the metal insert 85 and a recess connection 87. 8 and 9 show the tool member 55 (according to FIGS. 1-7) as dashed lines; In this case, the insert 85 can be formed separately according to the tool member 55.

In the following, the mode of operation of the sheet bending apparatus 1 will be explained according to the reference drawings of FIGS. 5 to 7 together with FIGS. 2 and 3 (the left bending punch 19 is shown in a covered state). .

The starting position or the stopping position of the sheet bending apparatus 1 is shown by the solid line in FIG. The upper counter punch 10 assumes that the stop position is raised from the plate 18, in which the metal plate 18 to be bent is supplied manually or automatically to the bending device 1, Stopped in position. The sheet bending cycle is started, and first, the counter punch 10 is moved downward by the spindle drive 14 (see FIG. 1) to contact the plate 18 to be bent, and the edge 13 thereof has a lower bending punch ( 19) 20 on. In this step, the plate 18 is virtually positioned between three punches or tools 10, 29 and 20 as shown in the clamp door 5, where the counter punch 10 is It is shown as a dotted line.

After this step, the racks for the lower bending punches 19 and 20 and the drive shafts 27 and 28 of the pinion drive device 24 are driven and driven, so that the gear racks 61 and 62 are slide grooves. (78) (see FIG. 3), the left punch 19 is rotated clockwise as shown in the bending punches 19 and 20 in opposite directions, i.e., in FIGS. , The right bending punch 20 is rotated about the common rotation shaft 21 to rotate counterclockwise. With the aid of the rotating lower tools 19, 20, the plate 18 is bent symmetrically. The bending edge 22 is formed by being supported with respect to the lower edge 13 of the upper counter punch 10. (See Fig. 6.) During this bending process, the counter perch 10 is suitably provided with a spindle drive ( 14) fixed or stationary in place by means (see Fig. 1), so that a fixed counter support is provided during bending operation. The plate 18 is bent at approximately 90 ° along the bending edge 22 (see FIG. 6); an acute angle of bend can be formed on the plate 18 as shown in FIG. Do.

If the plate 18 has already been bent, a so-called collision casing may occur, in which the bending edge 34 shown in FIGS. 5 to 7 hits the counterpunch 10 during the bending process. In order to further prevent undesired deformation in the sheet when further driving the bending punches 19 and 20, for example, the upper counter punch 10 is mounted so as to be rotatable about a horizontal axis so that the corner 34 Collision level can be avoided if

In order to prevent the counterpunch 10 from being damaged, a pivot bearing is required in this case, and various alternatives can be provided for such a collision phenomenon. It is beneficial to have a balance of forces; Thus, in addition to the operating mode in which the lower bending punches 19 and 20 are symmetrically driven in both opposite directions, in particular at the same angular velocity, it is also possible to implement an asymmetrical operation mode, as a whole, only relatively small horizontal components. Because only the action of the will remain. In view of this, the independent pivot drive device is characterized by two bending punches (2) driven by independent drive motors (72) (73) and independent shaft (27) (28) driven by the plate bending device (1). 19) (20) is made in the preferred embodiment.

As a result, when the sheet edge 34 hits one side of the counter punch 10 in the collision case as shown in FIG. 7, the bending punch 20 located on its side stops, and only the opposite side is bent. Only the punch 19 is further rotated to continue the bending operation on the plate 18 as shown in FIG.

Instead, however, the two bend punches 19 and 20 are rotated at different speeds from the starting point (figure 5) to reach a final position as shown in FIG. Of course you can. Further, after reaching the state shown in FIG. 7, the counter punch 10 is released from the rising door plate surface 18, and thereafter, the two bending punches 19 and 20 are straddling. It may be further configured to rotate upwards to form a fold in the region of the bend edge 22, ie the plate edge on the left side shown in FIG. 7 is folded directly to the remaining plate 18 portion. will be. In this bending step, the plate 18 in which the friction forces applied on the plate in the contact area 84 are largely folded can be sufficiently fixed and supported without the need for the counter punch 10 between the bending punches 19 and 20. Yes it turned out.

According to the bending apparatus 1 of the present invention, in performing bending bending (see FIGS. 5 and 6), the sheet contact area 84 at the stop position of the bending punches 19 and 20 (figure 5). It is also important that the silver forms a bearing or seating plane 91 for the plate 18 and enters the hinge connection 53 through the recess 90.

When the bending operation is performed, the recess 90 provides a room for the plate 18 within the region of the bending edge 22 to be manufactured so that the bending deviations adjacent to each other flatten the upper surface thereof. Squeeze phenomenon of the plate material 18, which may occur when forming, is prevented. Furthermore, from FIG. 5 the hinge pin or pivot shaft 21 extends somewhat below the plate contact plane 91 formed by the contact area 84 (ie, the lower side of the plate 18 in FIG. 5). It can be readily seen that a lever arm which is very suitable for transmitting the bending moment on the plate 18 during the bending operation can be obtained.

After the bending operation is finished, some of the drives used for the punches 10, 19 and 20 are reversed to rotate so that the lower bending punches 19 and 20 return to the vertical starting position according to the fifth. , Raises the upper counter punch 10 (if there is no further work)

Next, the bending plate 18 is moved to a subsequent bending position or removed from the bending device 1.

10 to 13 additionally show the important operating components of the sheet bending apparatus 1, the relative movement of the punch or tool 10, 19, 20 is completely consistent with the above-described embodiment, However, the fixed stop during the bending operation is not the upper counter punch 10, but one lower bending punch, the lower right bending punch 20 according to FIGS. 10 to 13, and the other lower bending punch 19. Is rotated in the same manner as the above-described embodiment during the bending operation of the plate 18 (see FIGS. 11 to 13), and further, the upper counter punch 10 is adapted to induce a relative rotational movement between the punches. Preferably, it is rotationally driven at 1/2 the angular velocity relative to the angular velocity of the lower left bend punch 19, the reference drawing of which shows three punches in the intermediate position in FIG. 12 and the final position in FIG.Shown in the state.

If the operating cycle is observed from the upper counter punch 10 (stop position) as an embodiment according to FIGS. 10 to 13, the results of the rotational operating cycle as described with reference to FIGS. You get However, in Figs. 10 to 13, each operating step is shown in a state observed from a fixed frame (not shown in detail in Figs. 10 to 13). Only a small amount of movement in a kinematic system in the same manner as in the bending apparatus of FIGS. 10 to 13 is required if it should be formed on one side of the bending edge on the plate 18 to be bent, if any . More specifically, in the embodiment shown in Figs. 10 to 13, the hinge holes 52 (eye members) in which the two lower bend punches 19 and 20 form the hinge connection part 53 again, and The hinge pins 54 extending through the entire hinge assembly are interconnected by interconnection. To the side of the hinge connection portion 53, two bending punches 19 and 20 have a curved circular shape and contact the plate 18 to be bent. In view of an easy replacement operation, the two bending punches 19, 20 can be assembled with their respective tool members 55, which firmly with the tool support or punch lower 56, eg the bolt 57 means. Combined by As a pivot driving device for the left lower punch 19, a tooth is provided, although not shown in detail, on the lower side of the arc-shaped guide rail 58, and in the base 56 of the other bending punch 20. It extends through the formed guide hole 59, and engages with the drive tooth wheel 60, which basically coincides with the tooth wheels 63 and 64 in FIGS. The drive device for the cogwheel 60 is operable through a drive motor not shown in detail and the gears already described with reference to FIGS. 1 to 9. FIG. 10 also shows how the left punch 19 faces outward, ie away from the right punch 20, as dashed lines, wherein the cogwheel 60 is then rotated counterclockwise (see arrow). )

For simplicity of configuration, although not shown, at the same time as the rotational drive of one lower punch 19, the upper punch 10 is preferably at a half angle of the lower punch 19 as mentioned above. Is rotated.

Basically, the driving of the upper punch 10 can be made in a manner similar to the driving of the lower punch 19, whereby a preferable transmission ratio of 2: 1 is ensured by the gear means. Since such a drive assembly is basically the same as the conventional one, it will not be described in more detail.

In addition, the configuration in which the upper punch 10 is mounted in the frame (not shown in detail) in the bending device shown in FIG. 10 is endably rotatably mounted on the lower frame 2 in the manner described in FIG. It is made in a manner similar to that of the side main support 3, 4, and is mounted together with a spindle drive (14 in FIG. 1) or similar drive known in the art.

11 to 13, a rotating shaft 21 for relative rotational operation is shown between the daily bending punches 19 and 20, in which case the hinge pins 54 of the hinge connecting portion 53 are formed. Coincides with the geometrical axis (Figure 10). During the bending operation, the upper punch 10 is also rotated as shown in FIGS. 12 to 13 degrees about the rotation shaft 21.

The center of the arc rail 58 is, of course, located on this pivot axis 21 (ie on the geometric axis of the hinge joint axis 54).

Although described in detail through the above-described particular preferred embodiment of the present invention, various modifications and variations are possible within the scope of the present invention.

Thus, for example, the hinge connecting portion 53 according to FIGS. 1 to 9 may be provided with a through hinge pin 54 having a length corresponding to the width of the bending device.

On the other hand, in the hinge connection portion (see FIG. 4) uniformly positioned, each of the hinge pins 54 protrudes to one side slightly beyond the tool member pair 55, and the continuous hinge hole 52 of the tool member 55 It can be reached in pairs so that a connection can be formed between each pair of tool members.

In addition, instead of the vertical structure of the bending device 1 in which the plate 18 to be bent should be horizontally positioned as described above, a structure having an arbitrary inclination angle is selectable, wherein the plate 18 to be bent is It is mounted at an angle to the starting position.

For this purpose, only the frame part can be modified.

Appropriate electrical control circuits may be provided to the drive motors, for example drive motors 72 and 73 to rotate the bending punches 19 and 20 and to the drive motors for the two spindle drive 14. These drive motors are shown to be turned on and off as needed. Also, basically, such electric drive motors, of course, can be replaced by a hydraulic motor or a hydraulic cylinder.

In addition, the upper punch 10 can be moved up and down by, for example, an eccentric drive or an actuating cylinder means, and in the lower operating positions in FIGS. 2, 3, 6 and 7 degrees. If the upper punch 10 is to be fixed, this can be achieved by simply stopping the eccentric drive in this position.

In the embodiment shown in FIG. 1, the width of the device was 1500 mm, the length of the tool member 55 was 125 mm, and the diameter of the hinge pin 54 was 8 mm; The pitch of the pivot drive device was 400 mm and was offset approximately 150 mm with respect to the end side of the device 1 of each of the outer drive units.

The total weight of the bending device 1 was 500 kg or less, and the plate of 2 mm thickness was formed without any difficulty.

Claims (13)

Plate material having three pinches 19, 20, 10, i.e., two adjacently arranged and rotatably connected bending punches 19, 20, wherein the bending punch has a plate contact area at the stop position. Forming a plane 91 and having a counter pinch 10 positioned against the vermiculite punches 19 and 20, the counter pinch being linearly movable between an operating position and a retracted position in the sheet material, Two punches 19, 20: 10, 19 are mounted so that the pivot drive device is rotatable, respectively, and the plate is rotated at least one of the bending punches 19, 20 around the counter punch in the operating position. In the sheet bending device that is bent by bending, the two bending punches (19, 20) in the stop position each of the corners are opposed to each other, the hinge connection portion 53 offset from the plate support plane (91) To the full width of the bending device (1) Hitting and directly connected to each other, a recess 90 is formed between the plate contact region 84 and the hinge connection portion 53 of the bending punches 19 and 20 in the bending punches 19 and 20, and the bending punch 19 (20) is equipped with detachable tool members (55) arranged adjacent over the full width of the bending device (1), the tool members being connected to each other in pairs by hinged connections, the bending punches (19, 20) Hinge connecting portion 53 is a plate bending device, characterized in that formed by the hinge connection of all tool member pairs. 2. The counter punch (10) according to claim 1, wherein several pivot drive devices (24) are connected to each of two independently rotatable bending punches (19, 20) over the full width of the bending device (1). The bending device, characterized in that only linearly movable. The bending method of claim 2, wherein the counter punch 10 is configured to be separated and retracted from the bending punches 19 and 20 so as to fold the plate 18 in the last bending step of the plate 18. Device. According to claim 1, wherein any one of the bending punch 20 is fixedly mounted, the other bending punch 19 is mounted to be rotatable like the counter punch 10, the rotatable bending punch (19) Is a bending device, characterized in that the rotational drive at an angular speed of twice the counter punch (10). The simple plug-in connection according to any one of claims 1 to 4, wherein the supply member (55) is located at a side opposite to the plate contact region (84) on the bending punches (19, 20) serving as a tool support. in connection (82,83), i.e. held by means of a tongue-and-groove connection. 2. The bending device according to claim 1, wherein the tool member pair is provided with hinge pins (54) corresponding to the length of the tool member. The bending device according to claim 6, wherein the hinge pins (54) of the tool member are projected and inserted into the hinge holes (52) of the pair of adjacent tool members on one side, respectively. 2. The bending device according to claim 1, wherein one common through hinge pin (54) is provided in all of the tool members (55). 2. The bending device according to claim 1, wherein the tool member (55) is provided with a detachable insert (85) for forming a plate contact region (84). 10. The bending apparatus according to claim 9, wherein the inserts (85) are screwed to the tool members (55), respectively. 2. The bending punches 19, 20 and 19, which are connected to each other, are provided with arcuate toothed rails 61, 62: 58 as pivot driving devices, respectively, and are firmly connected to each other. Bending device, characterized in that driven by the pinion (63, 64: 60) mounted respectively. 12. The bending device according to claim 11, wherein the toothed rails (61, 62) are mounted in an arcuate bearing, ie bearing groove (78), of a stationary bearing member (75) mounted on a frame (2). 12. Bending apparatus according to claim 11, characterized in that two separate electric motors (72,73) are provided for rotatably driving two shafts (27,28) connected to the bending punch (19,20).