SK98193A3 - Sheet-metal bending device - Google Patents

Abstract

The description relates to a sheet-metal bending device (1) with two bending punches (19, 20) interconnected so as to pivot which are arranged side by side and at least one of which is pivotably arranged and coupled to a pivot drive (24) and with a counter punch (10) opposite the bending punches (19, 20) and arranged to be linearly movable between a working position on the sheet metal (18) and a withdrawn position, about which the sheet metal (18) is bent in the working position, whereby the two bending punches (19, 20) are directly secured together via a hinged joint (53) in the working region along their edges which face each other in the inoperative position.

Description

Sheet metal bending machine

Technical field

BACKGROUND OF THE INVENTION The invention relates to a three-jaw sheet bending machine with two pivotably connected bending jaws arranged side-by-side and defining a bearing plane of the sheet in the resting position with one another, and one jaw and jaw counter-jaw, arranged linearly movably between the working position on the sheet and withdrawn

position, taking the two jaws are arranged pivotable and connected always with one drive for pivoting movement. and taking around the supporting jaw the sheet is in the working position by tilting at least one bending jaws bent.

BACKGROUND OF THE INVENTION

The most well-known and widespread technique of sheet metal bending or folding is to move against a sheet lying on the upper bending jaw with a lower die, the jaw pushing the sheet in the region of the formed hinge edge (see e.g. FR-A-2 201 973 but also US-A-2 649 128) to bend the sheet.

in all cases, it is generally not necessary to produce well-defined or sharp edges, that only one specific bend, i.e. a precisely determined bending angle, can be produced with one die, and that a significant portion of the energy generated is lost by friction on the die. These described disadvantages also exist in principle in those die systems in which the die is divided into two die parts arranged movably, in particular pivotably connected to one another. Such solutions are disclosed, for example, in DE-C-115 961 or even EP-A-379, 886.

s

FR-A-1 221 933 and DE-A-1 402 118 and DE-A-2 418 668, respectively.

US-A-1,045,089. US-A-1,258,892. US-A-1,633,744. US-A-2,433,841. JP-A-62-127125, JP-A-63-36923 and JP- A-63-199028. In all these constructions, the actual bending is performed from above by a bending jaw, which must be robust and equipped with an appropriately strong servo drive.

Also known is a bending machine for bending already profiled sheets (WO 81/02535) in order to be able to provide these profiled sheets with a corrugation, wherein the upper jaw, movable upwards, cooperates with the stationary lower jaw and on both sides arranged with a wider range. i * mouth.

diagonally up and down in the direction of its main plane.

«While the upper jaw, with the opposed stationary lower jaw, forms a corrugation of the plate, both sides are inclined

-r and other jaws externally i e.

For the simple bending of a sheet with the sharpest possible edge, this is not known, therefore it is not suitable for this purpose.

Furthermore, hand-operated pivoting bending machines are known, for example US-A-3,877,279, in which the sheet to be bent is clamped between the fixed lower jaw and the actual deflection of the lower jaw and the lower bending jaw itself. Furthermore, bending machines for bending have been proposed in US-A-3 044 526 or DE-A-1 40'2 838, US-A-3 282 076, GB-A-1 119 811 and GB-A-2 050 887. 2) in which the two lower bending jaws are pivotable against each other about horizontal axes so that the bent sheet can be bent around the opposing upper support jaw. Thereafter, the bearings for rotatably supporting the two lower bending jaws are arranged on both ends on the outside of the bending machine, and on these end faces there are also drives for pivoting movement in the form of working rolls. The disadvantage of this solution, however, is first and foremost that the bending jaws must be designed as extremely massive, especially when necessary. so that the machine has a wider width (eg 1 m or 3 m).

However, in the meantime, destroyed in the central region cannot be achieved;

precise bending of the sheet.

taking in this medium?

that is, the bent sheet has then.

bend length, curved convex shape.

With regard to the necessary mass of the bending jaws, the width of the bending machine is generally limited due to the required weight i, that the width of the bending machine above m can hardly be achieved because the total weight of the device would be excessively increased. This would result in bending machines weighing 15,000 to 20

000 kg or more.

SUMMARY OF THE INVENTION It is an object of the invention to provide the sheets described above with the formation of sharp edges of energy, in particular the massive design of the jaws required by multiple folding, which can bring weight. This bending machine by the most gentle sheet metal processing create a bending kind. which using be and will be and the bending machine will allow bending of relatively small expended sheets produced by various profiles bending machine will be even u and. for CO, in particular having a substantially smaller rack than hitherto a substantial reduction in total should also be characterized by what to bend.

SUMMARY OF THE INVENTION

This task is accomplished by a three-jaw sheet bending machine with two pivotably connected bending jaws. arranged adjacent to each other and defining with the sheet metal contact zones in a resting position abutting the plane of the sheet metal. and one supporting jaw, opposed to the bending jaws, and arranged linearly movable therebetween. a working position on the sheet metal and a retracted position, wherein the two jaws are arranged pivotally and connected to a single drive for the pivotal movement. and wherein the sheet is bent around the support jaw in the working position by pivoting the at least one bending jaw. according to the invention. The principle is that the two bending jaws are directly articulated to each other along their facing edges parallel to the rest position along the width of the bending machine. A recess in the bending jaw is provided in the bending jaws of the bending jaws, provided that the bending jaws are provided with removable tool segments arranged along the width of the bending machine which are joined together.

wherein the hinge joints of all the pairs of segments form the hinge joint of the bending jaws.

Thus, in the bending machine according to the invention, the working hinge joint of the two bending jaws is provided with a working area, whereby the hinge is subjected to a force flow when bending the sheets.

which causes at least partially equalization of the horizontal components of the bending forces in the hinge joint, which is essential, directly in the working area, as a result of which the bearing for the pivot bearing on the end faces of the bending jaws oynot, both solid and bending jaws. Experiments have shown that, when compared to e.g. 1 and 000 kg, the same bending power can be achieved with a bending machine according to the invention having a weight of up to 1/10. In addition, by moving the hinge joint from the plate seating plane and making a recess in the bending jaws, a gentle treatment of the sheets during bending as well as an optimum displacement of the forces at the beginning of the bending is achieved.

Equipped with bending jaws of the tool and segment units, which are articulated in pairs to each other, it is possible to change the bending machine more quickly, which makes it possible to adapt the bending machine to various working machines.

As far as the desired weight reduction is concerned, a plurality of actuators for the pivoting movement, which are distributed over the width of the bending machine, are provided in each case on the two independently pivoting bending jaws.

the supporting jaw being only non-linear.

plch his own already more times.

exercise bent

Order to do so. that the bending of the second or third bend strikes the support jaw in part (the so-called case did not occur).

for example, the supporting oscillations m are deflected. For this purpose, however, it is necessary to provide a pivot bearing on the support jaw, and both the pivot bearing and the jaw itself must be adequately sized so that it can also exert a support force when bending the sheet.

At the same time, however, it is necessary to ensure several times, although not necessarily, at least advantageously,

Even the uneven mobility of the support jaw and, in the event of such a collision, the possibility of a bent sheet metal to be priced.

In the event of a further bending over the support jaw, it is advantageous if the two bending jaws are equipped with non-interlocking drives for their pivotal movement. By means of these independent movements it is then possible to simply stop one bending jaw in the event of a collision, so that it is on the side of the bending jaw.

where the side of the plate with its already bent part is located. the sheet is then simply held, whereby the second bending jaw can be pivoted further and the sheet can be bent further.

Also in this asymmetric mode of operation, at least a major part of the horizontal deflection components that are produced is compensated by a hinge, so that only relatively small compensators of the generated forces are guided into the bending jaws and into the rack.

Another advantageous embodiment of the bending machine. which is non-covalently equivalent to the described embodiment with respect to

The formation of stationary parts of the machine in certain cases (due to the stationary fixation of one part of the sheet during bending) is characterized in that one bending jaw is provided as stationary and the other bending jaw and support jaw is driven at twice the angular speed than the supporting jaw.

Generally speaking, the bending machine according to the invention is particularly suitable with regard to the hinged connection for particularly extreme bending, and is particularly advantageous at that time. when the support jaw is adapted to be detachable from the bending jaws to allow movement of the sheet in the final phase of bending the sheet.

In the bending machine according to the invention, due to the joint of the bending jaws, it is advantageous to have the tooling on the sides of the bending jaws, acting as a tool holder, opposite to the sheet metal contact zones.

In order to facilitate the assembly and replacement of the tool segments, it is preferred that the pairs of tool segments are provided with length-adjusted hinge axes, when the hinge axes of the tool segments are always protruding on one side into the interconnected pairs of tool segments. When changing a tool, it is then possible, for example, to suspend all hinges i

the axes that are aligned with each other can be shifted linearly by the amount they project into the adjacent segment until the connection is disconnected.

Furthermore, for reasons of stability, it is also advantageous if a common through hinge axis is provided which extends through all tool segments.

In order to enable an advantageous exchange with respect to wear during operation, it is furthermore advantageous if the tool segments are provided with special extensions forming the contact zones of the sheet. These extensions can be screwed onto the tool segments.

It has proved to be a particularly advantageous drive option if the drive for pivoting movement is provided in each case with an arcuate toothed guide which is fixedly connected to the respective bending jaw and which is driven by a pinion mounted on the shaft. It is particularly preferred that ^- the gear is stored in the ring lead deposit, e.g. úiožnej groove, the stationary bearing part.

In this way, the corresponding bending jaw is mounted on the upright bend of the machine by means of toothed guides. Furthermore, it is also advantageous to provide the drives of both shafts associated with the bending jaws with two separate electric motors.

BRIEF DESCRIPTION OF THE DRAWINGS

BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be described in more detail with reference to the accompanying drawings, in which: FIG. 1 is a schematic perspective overview of a bending machine for bending sheet metal according to the invention in the rest state, FIG. 2 is a schematic perspective view of a part of a bending machine in the region of the bending tools, in the operating position, as compared to FIG. 1 on an enlarged scale, FIG. 3 is a schematic front view of the main part of the bending machine of FIG. 1 and 2, FIG. 4 shows, in the open state, a pair of hinged tool segments for the bending jaws of the bending machine of FIG.

to FIG. 5, 6 and 7 are schematic front views of bending jaws, i.e. tools and sheet, to be bent at different bending stages.

Fig. 8 is a front view of one bending jaw of the bending machine of FIG. 1 to 7, but in a modified embodiment from FIG. 1 to 7, FIG. 9 shows a modified embodiment of the bending jaw compared to FIG. 8 in the same front view.

Fig. 10 is a schematic perspective view of an arrangement of bending tools of another modified bending machine and the like;

11, v

7, by the machine according to

10, schematic front views, various stages of bending sheet metal by bending, wherein FIG. 11 shows the starting position, FIG. 12 between the polon and FIG. 13 end position.

According to FIG. 1 consists of a bending machine 7. that is, the bending apparatus and the bending press. as they are now referred to, for bending sheets from the lower stand 2, on which there are guides 5 in the front main beams.

in which the upper tool holder 9 is guided with an adjusting tool (also called an upper tool) in the form of a support jaw 10.

sliding vertically up and down. This support jaw 10 is preferably displaceably mounted on the tool holder 9 but can be made in one piece with it. Preferably, this support jaw 10 is further provided with a less or more sharp lower bending edge Γ3 (see Fig. 3).

however, it may have a different cross-sectional shape depending on the bend being formed.

For example, conventional spindle drives 14 are provided to move the upper support jaw W up and down. These spindle drives 14 are in this case provided with a spindle 16, driven, for example, by an electric drive motor, optionally via a gearbox and a clutch (not shown). These spindles 16 cooperate with the mats

17 connected to the tool holder 9 to be supported by the spindle. 16 jaw spindle drives on stand 2.

For bending and thrust drives up and down and other sheet metal drive 1S (Fig. O modified another, lower bending plate).

bending swivel knife. s L o j ο. and further on, with the pivot axis 21 being rotatable (see FIG. 5 of the formed edge) and which lies in the plane 23 of the support jaw 10.

For the drive of the jaws 19, the specifications which the walls up to 7) are further on the jaw stand 19, in the mold are stored which will be pivoted to which sheet (Fig. 3 and

18th

(5) by lines of,.

causing the pivot but less described about the common lies in the region slightly below, the upward and downward movement of the lower bending common pivot axis 21 serves a pivot mechanism which in the given embodiment comprises in the form of toothed racks and a width bending machine and

1, see FIG. 1 to

3. There is always one circular shape

62, i.e. the toothed segments, fixedly fixed at the bottom of the respective lower bending jaw i

19, 2Q. as shown in up to 3, and in fact FIG.

and 9.

in the same way

These toothed racks 62 are engaged with respective wheels or pinions 63, 64 mounted on a shaft of fire 19.

Both shafts 27, 28 are driven by a single electric drive motor

27, 28 extend at the end faces and, for example, at intermediate points, in the region of the individual drives 24 by means of toothed racks 61, 62 rotatable in the respective bearing parts more or less, in the case of one tooth rod 61,

64th

firmly fixed to the ground with 1 leather

such drives are evenly distributed. Thus, when driven by rotation h, the toothed racks 61 move along a circular path, the center of which rotates a.

123 g? ω e. · v y C Θ oscillating bending jaws i

2C) associated with them, in particular in the style shown in FIG. 5 (rest position) and FIG. 6 and 7 (swiveling study room).

To the above mentioned u ožň i u shafts

27, 28 ' on the one hand, the bending jaws on the stand fixedly mounted on a fixed crossbeam within the drive 24 width of the bending machine 1. a plurality of cross bearings 77 replaceable by a removable lid 76 (see also FIGS. 3), for the shafts 27, 28 and, on the other hand, they are provided on both sides with arcuate grooves 1 (see FIG. 2 on the right), in which the sliding toothed racks are of correspondingly circular shape. In this case, the rods 61, 62 are provided for each bearing part

1 arrangement. with relatively rigid toothed bars

61, the chucks 79, and the gripper is therefore provided with a gripper and a chain. is distributed uniformly over the entire width of the bending machine 1 so that forces are transmitted uniformly to the rack 2 in its crossbeam 74.

Therefore, a relatively relatively low-weight design of the storage elements is also sufficient.

It should be noted that in FIG. 3, only the pinion 63 associated with the shaft 27, which is also shown on the corium, is visible. 1 and 2 in front of the storage member 75, wherein in FIG. 3, a pinion 64 is associated with a shaft 28, which is located behind the bearing part 75, indicated only by dashed lines. On the other hand, FIG. 3 at right in FIG.

Next it is from obi '. 3 shows that both shafts 2 ?.

The cross-section in the form of the so-called should have a pinion 63, 64 fixedly mounted on the shafts 27, 28 without having a groove in the connection. The respective bending jaws 19 with toothed racks 61 can be supported, for example, by simple plug-in fit.

but also by means of fixed storage.

between the toothed rack mounting lugs, FIG.

Ó ô.

9 ·· can be screwed.

that both bending jaws 19.

are articulated to each other along their longitudinal upper inner edges by means of a hinge joint 53. 4, there are provided interlocking eyelets 52 which interpose the interlocking axis 54 in the assembled state. This interlocking joint 53 with the interlocking axis 54 defines the aforementioned axis of rotation about which the two pressing jaws are arranged.

1 oscillates during operation

In particular, the bending jaws 19, 20 are both interchangeable and tooling, and that the tool segments 55 are articulated to each other by pairs via hinge axes 54 a length adapted to their length.

These tool segments are fastened by means of a simple insert

In connection with the longitudinal tongue 32 and the groove 33 in the bending jaw 19 or 20 in operation, the change of the tooling turned out to be surprisingly unnecessary with the rigid segments 5 and with a good tool bending 19, and this is also related With this, at least their horizontal components are compensated, so that by means of a plug connection essentially only the vertical forces or forces which are running in the plane of the bending jaws of the groove 83 can be transmitted without further action. However, it may also be advantageous to provide the inserts with respect to wear during operation. The defective work on the sheet 18 (see, in addition to the embodiments by means of or s and 4, also FIG.

The coil 85 may also be carbide, and the screws 86 are connected to the tool segments o5 by the bending jaws.

1.9, 20 see fig. 8. On the other hand, a modified embodiment of the insert with an additional tongue joint 87 is a groove for a carbide insert 85. In this connection, FIG.

and 9 are further dashed to the loaded tool segments 50a of FIG. 1, however, can be divided into individual segments similar to tool segments 55.

The operation of the described bending machine 1 according to the schematic illustration in FIG. 5 to 7, and with reference to FIG. 2 and 3 (in which the left jaw 19 is shown pivoted).

the extruded or circular position of the sheet bending machine 1 is shown in FIG. 5 is shown in solid lines.

At the same time, the upper support of the log occupies, with a distance from the shoulder sheet 1S intended for bending, mechanically inserted and placed in the

liiciOné C’y’X 1 U.Í3 u; A y eyes n x and r * i ζ & Γιϊ. jaw 10 using spindle until st o j o u to 1 no u o hýi sheet metal 13. which was for; jaw 9, 20. This phase, clamped between three tools

20 is also in FIG. b with support jaw 10.

jaw 10 of its upper rest 13. a. in this position, the bending machine 1 can be manually or moved to the desired position. If now also the support 14 of the drive 14 (FIG. 1) moves downwards first.

it does not touch the bent edge of the bent laid on the lower bending in which the sheet 1 g is practically bending jaws 10. 19 and shown in dotted lines

Now the drive of the drive shafts 2 ?, 2S of the gear 24 for the lower bending jaws 19 is switched on. 20. The toothed racks 61 start. 62 can be moved in the sliding grooves 78 (FIG. 3), swinging the bending jaws 19, 20 in the opposite direction about their common axis of rotation 21, i.e., as shown in FIG. 5 and 6, the left bending jaw 9 is pivoted in a clockwise direction and the right bending jaw 20 is pivoted in a counterclockwise direction.

With the swiveling bending jaws 19.

the plate 18 is bent symmetrically against the lower support j, forming an error edge 22

PO2r i fig.6. During this bending with the cell Uo

W, by means of a spindle drive 1.4 (FIG.

in its position, it fixes or locks, during this bending of the fire along the bending edge 22, for example by about 90 °. see fig. 6. As further shown in FIG. 7, an acute bending angle can be formed on the sheet 18 without this further bending.

If the sheet 18 has previously been bent, see the already folded edge 34 in FIG. 5 to 7. there may be a so-called "collision" in which this already curved edge 34 encounters the support jaw 10 when bending the sheet 18. In order to avoid undesirable deformations of the sheet 13, for example, the upper support jaws 10 mounted rotatably about a horizontal axis. so that it could deflect on impact of the curved edge 34. However, in order not to have to be provided the pivoting bearings of the support jaw 10 required for this case. For this collision situation, another solution is provided, which advantageously performs a balancing of the forces by means of the hinge joint 53. Therefore, in addition to the described method of operation, the bending jaws 19, 20 can swing in opposite directions and symmetrically, especially at the same angular velocity. . the asymmetric way of working is allowed as well, since only a relatively small result horizon and zoning1 remain on the component

Therefore, in the described bending machine 7, the two bending jaws 19, 20 are preferably assigned to the drives. in the given embodiment, designed as drive motors 72, 73 and driven by them

2S. Consequently, in the described case, a collision is possible when the bent edge of the sheet 18 hits the support jaw 1.

P. set up the bending jaw 20 located on this side and pivot only the second bending jaw 19 so that the bending process of the sheet 18 can be completed, as shown in FIG.

Instead, it would also be possible to oscillate the two bending jaws 19, 20 from the beginning (FIG. 5) at different speeds in order to achieve the end position of FIG. 7th

5

It would also be possible, if the situation shown in FIG. 7. to move the support jaw 10 upwards from the sheet metal profile, 13. and then the two bending jaws 19, oscillate upward. whereby the left edge of the plate 18 in FIG.

the rest of the sheet 18.

With this friction acting on the sheet metal 8 by contacting and holding the already practically bent sheet metal, the bending machine 1 also begins to be significant, as described above, that the described contact zones 84 of sheet metal 18, which in the resting position of the bending jaws 19, 20 (FIG. O) define a bearing plane

9 plate

18. through the recess 90, the recesses 90 pass into the hinge joint of the recess 90, forming the plate 18 in the region of the bending edge to be formed, which does not wrinkle the plate 18, as eventually on the upper side, straight.

each other

19. 20.

Next is

Ξ fig. 5 it can be seen that the axis of the hinge joint 53 rotates and extends somewhat below the plate contact plane (t of the plate 18 in FIG. O), as determined by the touch zones 84, thereby producing suitable bending torque lever arms to the plate 18.

Upon completion of the bending operation, the various bore drives return their east and chock positions, so that the lower bending jaws 19, 20 swivel back to their vertical starting position, upwards (unless this has already occurred). The bent sheet 18 can now be moved to the next bending position in the machine and removed.

In FIG. 10 to 13, a further bending machine 1 with its essential workpieces is shown in a schematic manner which, in terms of the relative movement of its jaws 11, is shown. 19 and 20 fully correspond to the embodiment described above, but in this case, the upper support jaw is not bent

The IO is held as stationary, while one is held as stationary.

as shown in FIG. 10 to the right lower bending jaw 20, and the second lower bending jaw 19 oscillates similarly to the previously described embodiment when folding the sheet 18 (see FIGS. 1 to 13). and, in order to effect relative pivoting movements of the jaws relative to each other, the upper support jaw 10 - preferably at half the angular velocity, is swiveled by the lower bending jaw 19 - see also the limit of 1 bend of the three portions 10, 1.9, 20 shown in FIG. . 12 as well as the end position shown in FIG. 13th

At. observing the course of movements in this embodiment according to cbr. 10 to 13 from the upper support jaw (resting position), it is possible to illustrate the course of the oscillating movements similarly to the embodiment according to FIG.

to 9.

However, the uniform phases of movement are shown in FIG. 10 to 13 shown seen from the tacicary stand (b1 as would be even lower in FIGS. 10 to 13 ')

1. FIG.

as in the case of a bending machine up to 13, however, it is only necessary if the bent sheet is to make a movement on one side of the bending edge 22.

In detail, the embodiment according to FIG.

13 to 13, the two lower bending jaws 19, again articulated to one another by interlocking hinge eyes 52 to form the hinge joint 53, wherein the hinge axis 54 extends through the entire hinge joint arrangement 3.

Both bending jaws 19 are provided on the hinge sides.

where they touch

Both bending machines are V9

7 are likewise. due to easier interchangeability, assembled from the individual tool segments 55. firmly and that the basic lower part

56, for example by means of the lower left bending jaw 9, a circular water supply can be provided.

5S with b 1 on the underside, which extend through the guide slots 59 in any second bending jaw 20 and are engaged by drive gear sprockets 60, which in principle correspond to the gear sprockets 6 and 64 of FIG. 1 to 9. Drive these <>

FIG. 0 eVvQuVKy.

In FIG. 10 is also schematically indicated in dashed fashion as the left bending jaw 19 swivels when the pinion 60 is rotated counterclockwise.

20. It is shown that with this pivoting movement of one lower bending jaw 19, the upper supporting jaw 10 is also oscillating at the same time - as already mentioned, preferably at half an angular velocity as the bending jaw 19.

s

The drive of the upper support jaw 10 can in principle be analogous to that of the lower bending jaw 19, whereby a gear ratio of 2 = 1 is ensured by means of a transmission. The arrangement of the drive is customary, so it need not be further described here.

Furthermore, it is to be noted that the mounting of the upper support jaw 10 in a stand (not shown) in the bending machine 1 of FIG. 10 is in principle similar to the above-described example illustrated in FIG. 1, that is, by means of the main beams 3, 4 on the front, which, for example, could be pivoted on the lower rack 2 together with the spindle gear 14 (in FIG. 1) or a comparable drive.

In FIG. 11 to 13 also shows the pivot axis 21 of the relative pivoting movement of the lower bending jaws 19, 20.

that matches here s geometrickoľ. axis of the hinge axis 54 (FIG. 10) suspension joint 53. About this axis 21 of rotation at bending rotates the upper support jaw also oscillates 10. see

Fig. 12 and 13.

The center of the circular guide rails 58 lies, of course, on this axis of rotation 21, i.e. the geometric axis of the suspension axis 54).

Although described on special examples vy'dnot i i, it goes without saying.

other variations and modifications are also within its scope. For example, is it possible to provide the suspension hinge 53 with a transverse suspension hinge axis 4 corresponding to the length? width of the bending machine

1. Next, arrange the key (see

FIG.

4) it is also possible for the axis b4 to protrude on one side of the pair of tool segments 55 and could be plugged by the eyelets o2 of the adjacent one into the pair of tool segments 55. 55th

Furthermore, it is also possible, instead of the described vertical embodiment of the bending machine 1, wherein the bent sheet 18 is inserted horizontally therein, another arrangement, for example in principle inclined arrangement, with corresponding inclined insertion of the sheet 18 into the starting position. For this purpose, parts of the rack would need to be adapted accordingly.

For propulsion engines. that is, the drive motors 72, for pivoting the bending jaws 19, 20 as well as the drive motor or motors for both spindle drives 14, can be provided with respective electric control circuits so that these drive motors can be switched on and off as required. In principle, for example, hydraulic motors or pressure cylinders can also be used instead of these electric drive motors.

Furthermore, it is also possible to move up and down the upper support jaw 10, for example by means of an eccentric mechanism or a working roller. wherein the locking of the upper support jaw W in the lower operating position, for example according to FIG. 2, 3, 6 and 7 can be accomplished by simply shutting off the eccentric f

mechanism in this position.

In the practical example of FIG. 1 do 1 and the width of the bending machine 1. 1500 mm, the length of the tool segments 55 was 125 mm and the thickness of the hinge axis 54 was 8 mm.

The spacing of the drives 24 was 400 mm, with the outer working units always offset to the sides of the bending machine by about 10 mm.

The total weight of the bending machine X was less than 500 kg.

sheets 1J3 with a thickness of 2 mm.

Claims (13)

1. Bending C 1 L, a bending furnace of three or more jaws with a yard pivotally connected to each other by bending jaws and defining a contact plane of the sheet with the contact zones of the sheet at rest, and one end of the sheet, opposing bending jaws. and arranged linearly movably between the working position on the sheet and the withdrawn position, the two jaws being arranged pivotable and connected to one drive at a time for swinging movement. and ex 3 Π 3 í \ O I O O 3 G Γ - - í Cheers i ¾ £ - in washing machines: the shoulder h V> 'Kývr »Tue 1 X one ori "/ OOCEt jaw i bent , v y z c s a team. that both bending machines ľust e (19, 20) are along your i ch inverted edges, r ovnobež leg in rest position. in width bending machine (1) p r i amo mutually-klbovc connected suspension a joint (53) offset from the sheet (18), wherein between the bore holes (84) of the sheet (18) of each bending jaw ( 19, 20) and the hinge joint (53) is provided in the bending jaw (19) and that the bending jaws (19, 20) are provided with removable segments (55), tooled along the width of the bending machine (1) side by side, are coupled to each other in pairs by hinged joints, while hinging the xlaovc joints of all pairs of tool pendant joints (53) of the bending jaws (19.40). The bending machine according to claim 1, characterized in that a plurality of pivoting movement drives (24) distributed over the width of the bending machine (1) are supported on the two independently pivoting bending jaws (19, 20). and the support jaw (10) is movable only linearly. Bending machine according to claim 2, characterized in that. The support jaw (10) is adapted to be offset from the bending jaws (19, 20). to allow bending of the sheet (13) in the final sheet bending (1S) phase. The bending machine according to claim 1 (20) is supported sufficiently and the second bending jaw (19) is supported by the jaws (10) being pivoted, the pivotable bending jaw 19) is driven at twice the angular velocity as the support jaw (10). d. The bending machine according to claims 1 to 4. 5o) are fastened by means of, for example, a tongue (82) groove (83) on the side of the bending jaws (19. the sheet metal contact zones (84) Bending machine according to one of Claims 1 to 5, characterized in that: that the pairs of tool segments (55) are provided with their own hinge axis (54) adapted to their length. The bending machine according to claim 6, characterized in that the suspension axes (54) of the tool segments (55) in each case sieve into the hinge eyes (52) of the adjacent pair of tool segments (55). Bending machine according to one of Claims 1 to 5, characterized in that it is provided with a common intermediate suspension axis (54) extending through all the tool segments (55). Bending machine according to one of Claims 1 to 8. denoting that the tool segments (55) are Ο98Ή3 provided with special inserts (So) forming contact zones (84) .with sheet metal ( 18). (55) The bending machine according to claim 9, characterized in that the extensions (8o) are screwed. machine by are on toolbar 11. Bending z n and č u j ú c hyb -i Ä y - UPR Aven which is a firm One circular toothed rack connected to the respective bending machine of one of the claims 1 to 10 in γ- swinging ρο- (61. 53). čust lustou (i9. mounted on the shaft (27, 28) is driven. The bending machine according to claim 11, characterized in that the toothed racks (61, 62) are mounted in a circular bearing, for example in a bearing groove, in a stationary bearing piece located on the stand (2). The bending machine according to claim 11 or 12, characterized in that two separate electric motors (72, 73) are provided for rotational movement of the two shafts (27, 28) associated with the bending jaws (19, 20).