SI9210226A - Sheet-metal bending device - Google Patents

Abstract

A device for bending sheet metal is described with two mutually pivotally connected bendings pehalomas (19, 20), which are arranged second next to each other, and at least he erosionally wavered arranged and coupled by a pivoting drive (24), and s between the working position on the sheet (18) and back pull-out position linearly flexibly arranged, opposite the bending pegs (19, 20) standing antidržalnoh pehlim (10) around which it is in the working position folds the sheet (18), where are both bending pins (19, 20) along their v position of resting one another to the other edges in working area is directly interconnected via a hinge connection (53).

Description

Elevator Verkaufsgerate-Gesellschaft m.b.H.

P 226/92

Plate bending device

The invention relates to a device for bending sheet metal with interconnected bending blades, which are arranged secondly to each other and with the contact areas of the sheet at resting position, determine the contact plane of the sheet, of which at least one is bent and coupled to the oscillating drive, and with anti-grip pedestal, which is arranged linearly movable between the working position on the sheet metal and the retracted position, and which is opposite the bending glasses and around which the sheet metal is folded in the working position.

The best known and most widely used technique for sheet metal bending or bending exists in that the upper bending sheet moves towards the sheet lying on the lower recess, the bending sheet metal with the area of the bending edge being transformed presses into the recess (e.g. . FR-A-2 201 973 as well as US-A-2 649 128), thereby bending the sheet metal. The disadvantage is that by virtue of all the rules, no well-defined or sharp bending edges can be made, so that only one completely defined bending can be made on a single pit, i.e. a completely defined bending angle, and that further a considerable part of the energy input is lost by friction at drowning. The aforementioned drawbacks also relate essentially to those drowning devices in which the drowning is internally divided into two in the holder movably arranged, in particular also the oscillatingly interconnected drowning parts, cf. for example, file DE-C115 961 or also EP-A-379 886, FR-A-1221 933 or. DE-A-1 402 118, DE-A-2 418 668, 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 as well as JP-A-63-199028. For all of these structures, the bending work is introduced as such from the top bending pedal, which must be suitably robust and equipped with a suitably sized sizing actuator.

Bending apparatus for profiled sheet metal (WO 81/02535) is also known to provide corrugated sheet metal, wherein the upper, upward and downward moving blades interact with the stationary lower blades as well as with the lateral blades arranged in the direction thereof. their principal planes obliquely upward and downward moving additional girders. While the upper pedestal with the stationary lower pedestal, standing first opposite, forms a ripple in the sheet metal, the two lateral oblique pedals produce the next ripple. For easy bending of sheet metal with as sharp bending edge as possible, this known bending machine is not made and is not suitable.

Starting from swinging bending machines in which the bending sheet is clamped between the stationary lower bridge and the upper bridge, which stumbles against the first bridge and the lower bending bridge performs bending work, were then in US-A-3 files 044 526 oz. DE-A-1 402 838, US-A-3 282 076, GB-A-1 119 811 and GB-A-2 050 887 of the proposed sheet bending device in which the lower bending pedals can be pivotally rotated about the horizontal axes, so that the sheet ready to be bent is folded around the upper anti-theft pedal opposite them. The swinging bearings for the two lower bowls are arranged externally on both front faces of the bending device, and there are also swing cylinders in the form of working cylinders on these front sides. The disadvantage, in particular, is that the bending blades have to be made extremely massive, especially if larger machine widths (eg 2 m or 3 m) are desirable; however, no precise bending in the sheet metal is achievable in the middle of the machine, however. the bent sheet is generally even more open in this middle region than in the end region, i.e., the bent sheet then has a convex shape when viewed in terms of bending length. Together with the necessary massive design of bending blades, it is also considered that, on the basis of the required masses, the width of the machine is generally limited, i.e., machine widths beyond 3 m are hardly achievable, since the total mass of the preparation for this purpose would be excessively increased. The result would be bending machines weighing between 15 and 201 and above.

The aim of the invention is now to provide a device for bending sheet metal of the aforementioned type, which allows bending of sheet metal while producing sharp bending edges with relatively low energy consumption, in which the most various profiles can be feasible by means of multiple bending and based on as much as possible simple construction and requires, in particular, significantly less massive designs for the hull and frame than ever before, resulting in a significant reduction in weight. Further efforts are also made to ensure that bending sheets are treated as leniently as possible.

The device according to the invention for bending sheet metal of the aforementioned type is characterized in that the two bending blades in the working area are directly hinged to one another along their edges, which are in the rest position facing each other.

In the preparation for bending according to the invention, there is thus a hinge connection of the two bending blades in the working area, whereby through this shamir hinge connection, the bending of the plates gives a flow of forces, which leads to at least partial alignment of the horizontal components in the bending of the introduced forces in the hinge, viz. , which is essential, directly in the working area, thus rendering massive swinging bearings on one side of the bending arms and, on the other, of the massive implementation of the bending arms themselves. Experiments have shown that compared to bending machines with, for example, 15 t, the same bending capacity can be achieved with the inventive design of the bending device with a total mass of only about 2 t, which means a possible reduction in weight to 1/5 to 1/10.

In view of the intended weight reduction, it is also particularly advantageous if the two bending blades are independently rotatable, with the bending gears on the bending bobbin being reasonably distributed over the width of the bending device and the counter bladder moving only linearly.

In the case of multiple bending, the bending sheet, when making the second or third bend with an already bent, angularly swirled area, hits the anti-roller (the so-called collision case). This can be assisted, for example, by the fact that the anti-theft pedal can be removed by a swivel. However, this requires a swinging bearing of the anti-theft pedestal, and it is appropriate to dimension both the swinging bearing and the pedestal only to allow the counter to be introduced when bending the sheet. For a number of reasons, therefore, it is not strictly necessary, but this is preferably assumed to be aimed at the linear motility of the anti-roller only, and in this case to create the possibility of withdrawal for the bending sheet or the sheet. in order to allow further bending after being hit by the anti-grip pendulum, it is particularly advantageous according to the invention if both bending pendulums are arranged with mutually independent oscillating actuators. By means of independent oscillating actuators, it is then possible to easily hold one of the bending blades in the event of a collision, so that on the side of the bending blades, where the side of the sheet with the already bent section of the sheet is located, the sheet is then easily grabbed while the other bending blades twist further to allow the sheet to bend further. Even in this asymmetric mode, at least the majority of the horizontal components of the bending forces involved are compensated via the hinge joint, so that only relatively small force components are introduced into the bending cup and of these into the machine frame.

An embodiment which is kinematically equivalent to the above embodiments and, in certain cases (for example, due to the stationary fixation of one of the sections of the sheet during bending), is preferred in the case of the stationary part of the bending device, further characterized in that one of the bending pedals is arranged stationary, the other bending pedal as well as the anti-pedal pedal are pivotally mounted, with the oscillating bending pedal being driven at double angular velocity compared to the antistatic pedal.

Generally speaking, the bending device provided, due to the given joint connection, is suitable for particularly extreme bending operations, and it is particularly advantageous if the anti-grip pedal is pulled back from the sheet during the last bending phase to allow sheet metal to be bent.

For a gentle bending of sheet metal during bending, as well as to achieve optimum force transfer at the beginning of bending work, the sowing also proved to be advantageous if, for example, between. in the cross-section convexly curved, optionally flattened zone of contact with the sheet of each bending pendulum and the Hinge joint, the projected recess in the bending pendulum, the hinge pivot axis extending slightly offset from the plane of contact of the sheet.

It is further advantageous to allow the bending device to be rearranged rapidly, with various working widths being particularly feasible, if the bending blades are provided with the width of the bending device arranged apart from each other, removable tool segments. In the present bending arrangement, due to the inventive hinge joint of the bending blades, it is possible in the preferred sense that the tool segments are by a simple plug connection, 'e.g. grooves and pens joints held opposite to the contact zones of the sheet-metal side adjacent to the bending pedestals acting otherwise as tool holders.

In all the above-mentioned cases, the preferred embodiment is characterized in that the tool segments are hingedly interconnected, whereby the hinge joints of the bend blades are formed by the hinge joints of all two tool-segment pairs. In addition, it is easier to assemble as well as to replace, especially if the tool segment segments are provided with their own hinged axes adapted to the segment length. It is further advantageous to align the tool segments arranged side by side with the hinge axes of the tool segments projecting into the hinge ears of the connecting pair of tool segments on each side. For example, when changing tools, all hinged axes, which are aligned with each other, are then displaced linearly to the extent that the segments no longer fit together.

On the other hand, it may also be advantageous for stability reasons if a common hinge axis extending through all tool segments is provided.

It is also advantageous, in the view of wear and tear occurring during operation, to replace it in a convenient manner if the bending bowls or, as the case may be, the tool segments are provided with separate inserts forming the contact areas of the sheet. In this case, the inserts may be screwed onto the bending grips or tool segments.

A particularly advantageous, effective drive option has been proven to be a circular arc (as in each case) designed as a circular arch, which is tightly coupled to the associated bending pedal and is driven by a stepson sitting on a shaft. It is further advantageous if the toothed rail is mounted in a circular arc shaped bed, e.g. in the recess groove, on the stationary recess. In this way, the bending pendulum can be mounted on the frame of the bending device at the same time - via the toothed rails. It is also preferred that two separate electric motors are provided for the rotary drive of the two shaft bending shafts.

The invention will be further explained below on the basis of the illustrated, particularly preferred embodiment examples, in the drawings, to which the invention should not be limited. In doing so, they show:

FIG. 1 is a spatial representation of an apparatus as a whole according to the invention for bending a sheet in a stationary position;

FIG. 2 is a spatial representation of a section of this bending device in the range of bending tools in the working position and with respect to FIG. 1 on a larger scale;

FIG. 3 is a schematic front view of the main components of a bending device according to FIG. 1 and 2;

FIG. 4 in a separate extension view of the two tool segments with a hinge joint for the bending device of the bending device according to FIG. 1 to 3;

FIG. 5, 6, 7 in schematic front views, bending tools and bending sheet metal in various stages of bending work;

FIG. 8 is a front view of one of the bending arms of the bending device according to FIG. 1 to 7, but in an embodiment which compares with FIGS. 1 to 7 changes;

FIG. 9 is an embodiment that is in comparison with FIG. 8 modified, in an appropriate frontal view;

FIG. 10 is a schematic, spatial view of the arrangement of bending tools of a further, modified bending device; and FIG. 11,12,13 in schematic front views analogous to FIG. 5, 6 and 7 various bending stages of the sheet with the bending device according to FIG. 10, shown in FIG. 11, in FIG. 12 and in FIG. 13 final position.

According to FIG. 1 has a generally referred to as 1 sheet metal bending device, bending machine or bending press, which becomes particularly preferred, the lower frame 2, which has upright guides 5, 4 in which the upright guides 5 are provided in which it is movable upwards and the lower guided upper tool holder 9 s as a bridge or as a sword shaped anti-grip pedal 10 (also called an upper tool or simple sword). Preferably, this anti-grip pedestal 10 is mounted interchangeably on the tool holder 9, and may be provided in one piece; the blade is more or less similarly designed to the lower bending edge 13 (see Fig. 3), but depending on the intended bending, other cross-sectional shapes may be provided.

For example, up and down movements of the upper anti-theft pedestal 10 are provided, for example, as such conventional spindle gears, such as in FIG. 1 is schematically illustrated at 14. These spindle gears 14 comprise, for example, a spindle 16, which is optionally driven by a gearbox and clutch (not shown) from an electric drive motor and which cooperates with a spindle nut 17 connected to the tool holder 9. , so that when turning the spindle 16, the tool holder 9 with the anti-grip pedal 10 moves in guides 5 up or down. arr. These spindle gearboxes 14, as well as the further propulsion devices, which have yet to be explained, are arranged in a conventional manner in frame 2.

For bending the sheet 18 (see FIGS. 5 to 7), further on frame 2 provides two lower bending bows 19, 20, which are formed as plates or bridges. Both of these lower bending bows 19, 20 are pivotally mounted on frame 2, which will be further explained below, both of which are rotatable about the common oscillating axis 21 (see Figs. 5 to 7), which lies in the region of the future bending edge 22 in, but slightly below, the bending sheet 18, and which lies in particular with the guides 5, 6 of the fixed plane 23 (FIGS. 3 and 5) of the upward and downward movement of the anti-roller 10.

As a drive to rotate the lower bending pendulum 19, 20 around a common oscillating axis 21, a oscillating mechanism is provided which, in the present embodiment, comprises the widths of the bending device 1 - more in FIG. 1 to 3 schematically in 24 indicated gear drives in the form of gears with gear rack. In this case, in each case, a toothed rack or rail 61, 62 is firmly positioned in the lower region of the respective lower bending pendulum 19, respectively. 20, such as in FIG. 1 to 3, as shown in FIG. 8 and 9. These toothed laths or segments 61, 62 engage with each other as well as with bending hinges 19, 20 parallel beams 27 and. 28 seats, e.g. equal to large gears 63 oz. 64. Both shafts 27, 28 are each driven by e.g. electric drive motor 72 oz. 73, in the present case, through a closer non-displayed laptop, as shown in FIG.

1. The two shafts 27, 28 extend over the entire width of the bending device 1 and are rotatably mounted in the respective bearing portions 75 on frame 2, which are provided below, at the front as well as at the intermediate points, in the area of individual gearboxes 24 should be further explained. One toothed pole 61 or 24 comes to each gearbox 24. 62 as well as on the corresponding shaft 27 respectively. 28 rotatably mounted sprocket 63 oz. 64, and as mentioned above, several such gears 24 with a toothed shaft, as the gear unit intended, are distributed over the width of the bending device 1 to allow the input torque to be distributed. When rotating the shaft 27, 28, the gears 61, 62 therefore move in a circular arc-shaped line whose center lies on the oscillating axis 21, with the lower bending arms 19, 20 associated therewith rotating apart in a spacer support manner. , cf. especially the representations in FIG. 5 (idle state) as well as 6 and 7 (apart swing state).

For the bearing mentioned above, on one side of the shaft, 27, 28 or. on the second bending bows 19, 20 in frame 2, several fixed parts 75 extending transversely to the transverse carrier 74 are distributed on the fixed transverse beams 74 of the frame 2 at the points of gears 24 with gear widths across the width of the machine. on the one hand, through the removable bearing caps 76, the replaceable bearings 77 (see also Figs. 2 and 3) for the shafts 27,28, and on the other, in their upper region on both sides, are provided with circular arc shaped grooves 78 (see Fig. 2, right), in which the toothed laths or toothed segments 61, 62 are slidably guided as circular arches, with the aid provided therein, appropriately as the circular arc of formed guide wedges or guide laths 79. thus, each bearing portion 75 is then slidably guided by two gear segments 61, 62, one for shaft 27 and the other for shaft 28. Through this bearing arrangement, the relatively fixed toothed poles 61, 62 and their guide wedges a 79, as a circular arch shaped sliding grooves 78 oz. bearings in part 75, then the load absorption is then distributed along the width of the machine, so that, when bending, the forces to be absorbed appear to be distributed in frame 2 or. its transverse support 74. It is thus sufficient that the bearing components 75 are relatively relatively massive.

It will be mentioned that in the presentation in FIG. 3 shows only the shafts 27 of the adapted stepson 63, which is also shown in FIG. 1 and 2 in front of the bearing portion 75, and correspondingly in FIG. 3 Shafts 28 Adapted pinion 64 located behind this bearing portion

75, indicated only by dashed lines. On the other hand, from this presentation in FIG. 3 at the shaft 28, drawn there to the right, seen through the bearing cap 76, access bearing 77 for the shaft 28, cf. for the rest, the presentation in FIG. 2. Hereinafter referred to in FIG. 3 shows that both shafts 27, 28 are made with a cross-section in the form of a 'defined neo-circle with odd number of corners' ¹ , that the stepchildren are 63 or. 64 can be pivotally fixed without weakening the cross section, such as in the case of a wedge and groove connection. Each bending pendulum 19 oz. 20 may be with associated gear segment 61 or. 62 is adopted, for example, in a simple plug-in or impression fit between a toothed segment 61 or. 62 one-piece seat projections 80, 81, cf. except FIG. 3 also FIG. 8 and 9, but may also be screwed together.

From the presentation in FIG. 2 and 3, it is further apparent that the two bending bows 19, 20 are articulated interconnected through their upper, inner edges via a hinge joint 53, along the entire working width. According to FIG. 4, hinged ears or meshes 52 are provided therewith, through which the hinge axis 54 passes through in the assembled state. This hinge joint 53 with the hinge axis 54 defines the aforementioned oscillating axis 21 around which both bending axes are rotated. 19, 20.

In detail, the bending bows 19, 20 are designed as tool holders with separately removable, replaceable tool segments 55, the tool segments 55 being articulated in pairs in conjunction with the hinge axes 54, each of which is adapted thereto. These tool segments 55 are firmly held in the tool holders of the service bending holders 19 or 13 through a simple plug-in connection, with a longitudinally extending pen 82 and a corresponding groove 83. 20, so that the replacement of tool segments 55 can be carried out particularly easily and quickly. In doing so, it has been shown that a firm connection between the individual tool segments 55 and the respective tool holder, respectively. surprisingly, bending bows 19, 20 are not required, and this is also due to the fact that in operation from the forces involved in bending, the horizontal components are at least substantially compensated via the hinge joint 53 so that they are connected via a plug connection (pens 82, grooves 83) are essentially transmitted only by vertical forces

1. In orig .: i.e. Gleichdicks; instead of a translation of the term, an explanation of the password from the LUEGER technical encyclopedia is taken here.

oz. in the plane of the bending bowls 19 oz. 20 through the force of the described connection 82, 83 of the groove and the pen without feasibility. Depending on the wear and tear occurring, it may be advisable to provide tool inserts 85 which feed the bending work as such onto the sheet metal via contact zones 84 (see except Figs. 3 and 4, also Fig. 8), these inserts being 85 for example, inserts of hard metal that bolt through the bolts 86 to the tool segments 55 - or to the bending blades 19, 20, ch. FIG. 8. The embodiment of the inserts, which is modified against the aforementioned, with the additional connection 87 of the slot and the insert for the insert 85 of the solid metal is illustrated in FIG. 9. Herein, in FIG. 8 and 9 further with dashed lines indicate that in bending pedals, e.g. in the left bending pedal 19, tool segments 55 of FIG. 1 to 8, i.e. the bending bows 19 (and 20) then form the hinge joint 53 themselves; the inserts 85 are then all-time or correspondingly in FIG. 1 to 4 visible tool segments 55 segmented.

The following describes the operation of the described sheet bending apparatus 1 based on the schematic representation of FIG. 5 to 7 as well as in FIG. 2 and 3 (in which the left bending pedal 19 is shown rotated).

The starting or resting position of the sheet bending device 1 is in FIG. 5 illustrated by solid lines. In doing so, the upper anti-theft pedestal 10 has its upper idle position raised from the sheet 18, and in this position the intended plate 18 can be manually or mechanically brought into the bending device 1 and placed in the correct position thereon. If the plate bending cycle then begins, the anti-braking pedal 10 first moves downwards with the help of spindle gears 14 (Fig. 1) to reach with its edge 13 a bending plate 13 previously placed on the lower bending cup 19, 20. This phase, in which the sheet 18 is virtually clamped between the three cups or tools 10, 19 and 20, is also illustrated in FIG. 5 i.s. with dashed anti-grip pedal 10.

However, the drive to the drive shafts 27, 28 of the gearboxes 24 with the toothed rack for the lower bushings 19, 20 is now engaged. Accordingly, the bushings 61, 62 are driven along the sliding grooves 78 (Fig. 3), whereby the bending blades 19 , 20 counter-rotating around them the common oscillating axis 21, i after the presentation in FIG. 5 and 6, the left bending pedal 19 is rotated clockwise and the right bending pedal 20 counter-clockwise. With the help of the oscillating lower tools 19, 20, the sheet 18 is, for example, first symmetrically flexed when it rests on the lower edge 13 of the upper anti-theft bracket 10, producing a bending edge 22, see FIG. FIG. 6. During this bending operation, a suitable anti-grip pedal 10, for example by means of spindle gears 14 (Fig. 1), is fixed or arrested in its position so that in this bending operation it forms a stationary anti-grip. The sheet 18 is thereby folded for e.g. about 90 ° along the bending edge 22, cf. the representation in FIG. 6; as further illustrated in FIG. 7, the sharp bending angle of the sheet 18 can also be performed without further bending operation. If the sheet 18 has already undergone a bending operation, see FIG. the already bent edge 34 in FIG. 5 to 7, may occur by t.im. of a collision case in which this already bent edge 34 bends against the anti-firing bracket 10. In order to prevent undesirable deformation of the sheet metal 18 in further driving of the bending brackets 19, for example, the upper anti-bracket bracket 10 could be pivoted about a horizontal axis, thus that when hit 34, it could recede. However, in order to be able to waive the anti-roller bearing swivel 10 that would be required in this case, a further possibility of a solution can be provided for this collision case, with the advantage that the hinge joint 53 has a counterbalancing force; thus, in addition to the described operation, in which the lower bending arms 19, 20 are driven in an antisense and symmetrical manner, and in particular at the same angular velocity, asymmetric modes can be tolerated, leaving only one relatively small resultant horizontal component altogether. Thus, in the present sheet bending device 1, independent bending oscillators 19, 20 are preferably assigned independent oscillating actuators, in the present embodiment, by means of separate propulsion motors 72, 73 and shafts 27, 28 which drive them. Thus, in the case of the collision described, when the edge 34 of the sheet hits the side against the anti-bracket 10, see FIG. FIG. 7, hold the bending pedal 20 located on this side, and then only the second bending pedal 19 can be further rotated further to bring the bending operation on the sheet 18 to an end, as illustrated in FIG. 7.

Alternatively, it would also be possible to rotate the two bending bows 19, 20 from the beginning (Fig. 5) at different speeds to achieve a final position in continuous working stroke, for example according to Figs. 7.

In the given case, when achieved in FIG. 7 illustrates the situation, the anti-theft pedestal 10 can move upwards from the sheet profile 18, and then both bending cups 19, 20 are further rotated upwards in terms of burst support, thereby producing a bend in the area of the fabricated bending edge 22, i.e. the edge of the sheet of FIG. 7 left would then directly rest on the remaining plate 18. As it turned out, at this phase of flexing the friction force introduced onto the sheet via contact zones 84 is sufficient to hold the already far-bent plate 18 between the bending bows 19, 20 without the need for an anti-pedal pedal 10.

For beginning bending operation, cf. FIG. 5 and 6, it is also important in the present sheet bending device 1 that the sheet touching zone 84 described in the idle position of the bending cups 19, 20 (FIG. 5) define the plane 91 of the sheet metal contact or contact 18 via the recess 90 they go into the shammer joint 53. These recesses 90 create a space for sheet metal 18 in the starting bending region, so that the sheet metal 18 does not become crushed there, as might be the case with the bending pedals connected to one another. were on the upper side of the level. For the rest, FIG. 5 shows that the hinge axis or. the swinging axis 21 extends slightly below the sheet metal plane 91 defined by contact zones 84 (coinciding with the underside of the sheet 18 in FIG. 5), thus creating a more favorable lever arm for transferring the bending moment to the sheet 18 .

When the bending operation is completed, the various pendulum actuators 10, 19, 20 are reversed to rotate the lower pendulum blades 19, 20 back to the upright starting position of FIG. 5 as well as moving the upper anti-theft pedal 10 up (if this has not already happened). The bent sheet 18 can then be moved to the next bending position or removed from the bending device 1.

In FIG. 10 to 13, a schematic representation of its essential parts is a further device 1 for bending sheet metal, which in terms of the relative movement of its grips or tools 10, 19 and 20, corresponds exactly to the embodiment described above, but which does not have a stationary holding upper during the bending process. anti-holding pedal 10, but one of the lower ones, after the presentation in FIG. 10 to 13, the right lower bending pedal 20, while the second lower bending pedal 19, when bending the sheet 18 (see FIGS. 11 to 13), rotate in accordance with previous embodiments, and in addition to rotating the upper anti-pedal blades to perform relative oscillations between the blades. Fig. 10 shows a half angular velocity example 13 with the left lower bending pedal 19, see also FIG. 12 shows the intermediate position of the three goblets as in FIG. 13 final position shown. If, in this embodiment, FIG. 10 to 13 observe the movement of movement from the upper anti-theft pedestal 10 (rest position), a swinging motion similar to that described above based on FIG. 1 to 9. The individual motion phases are in FIG. 10 to 13 are shown by observation from a stationary frame (not illustrated in greater detail in FIGS. 10 to 13). Such kinematics as in the bending apparatus of FIG. 10 to 13 may be desirable if there is only a slight movement, if any, of the sheet metal 18 to be bent on one side of the bending edge.

In detail, in the embodiment of FIG. 10 to 13, the two lower bending bows 19, 20 are again hinged, with hinged ear members 52 in each other to form a hinge joint 53, pivotally interconnected, with the hinge axis 54 extending throughout the articulated arrangement. Sideways with respect to the hinge joint 53, both bending bows 19, 20 have a rounded design of the parts concerned where they come in contact with the bending-ready sheet. Both bending bows 19, 20 can thus be constructed with individual tool segments 55, which are tightly connected to the tool carrier or the lower part 56 of the hinge, for example by means of bolts 57, for ease of interchangeability. as a circular arc of the shaped guide rail 58 may be provided with a closer undersized tooth on the underside, extending through guide grooves 59 in the base portion 56 of the second bending pedal 20 and engaging with drive gears 60, which in principle correspond to gears 63 or. 64 according to FIG. 1 to 9. The drive for these gears 60 may follow in the manner already mentioned in connection with FIG. 1 through 9, through in FIG. 10 closer to the drive motor as well as the laptop.

In FIG. 10 is a schematic view of the dashed lines illustrating how, when rotating the sprocket 60 in the counter-sense (see arrow), the left pedal 19 is rotated out, i.e. away from the right goggle 20. For the sake of simplicity, it did not appear here that at the same time as the rotary movement of one of the lower goggles, goggles 19, the upper goggles 10 were rotated - as is said, reasonably at half angular velocity compared to the lower goggles 19.

The operation of the upper pedestal 10 may thus be carried out in a manner analogous in principle to that of the lower pedestal 19, whereby a 2: 1 gear ratio may be established via the laptop. The drive arrangement of this type is normal as such, so there is no need to interpret it further here.

Further, it should be noted that the mounting of the upper pedestal 10 is in a more closely shown frame in the bending arrangement of FIG. 10 may be provided in principle in the same manner as mentioned above with reference to FIG. 1, i.e. especially with the front main beams 3, 4, which should be positioned here, for example. together with the spindle actuators (14 in FIG. 1) or comparable actuators in the lower frame 2, which can be done in a manner close to the person skilled in the art.

In FIG. 11 to 13 also illustrates the oscillating axis 21 for relative rotation between the lower bending hinges 19, 20, which here coincides with the geometric axis of the hinge joint 54 (Fig. 10) of the hinge joint 53. The upper hinge is also rotated about this oscillating axis 21. 10, see the representation in FIG. 12 and FIG. 13.

It goes without saying that the center lies as the circular arc of the formed rails 58 on this oscillating axis 21 (i.e., the geometric axis of the axis 54 of the hinge joint 54).

Moreover, the invention is described above based on particularly preferred embodiments, but further variations and modifications are possible within the invention. Thus, for example, the hinge joint 53, described on the basis of FIG. 1 to 9, be fitted with a hinge axle 54 with a length corresponding to the width of the machine. On the other hand, for distributed hinge arrangements, cf. FIG. 4, it is also possible to allow the respective pivot joints 54 on one side to protrude slightly over the pairs of tool segment 55s and extend into the hinge eyes 52 of the next pair of tool segments 55, in such a way that the coupling between the two pairs of tool segments is achieved.

Furthermore, it is also possible to select a different orientation instead of the upright positioning of the bending device 1, whereby the prepared sheet 18 is inserted horizontally, for example in the case of an oblique arrangement, with an appropriate oblique placement of the sheet 18 in the starting position. Only parts of the framework should be modified accordingly.

Suitable electric control circuits may be provided for drive motors, such as drive motors 72, 73 for swivel bending bows 19, 20, as well as drive motors or drive motors for both spindle drives 14, so that these drive motors can be switched on and off as necessary. In principle, hydraulic motors and / or hydraulic motors can be taken for granted instead of these electric drive motors. cylinders for pressure medium.

In the rest, it is also possible for the upper pedestal 10 to move up and down, for example, by means of an eccentric drive or a working cylinder, in which case the upper pedal 10 may be locked in the lower operating position, e.g. according to FIG. 2, 3, 6 and 7, by simply disconnecting the eccentric drive in this position.

In a practical embodiment, FIG. 1, the width of the machine was 1500 mm, the length of the tool segments 55 was 125 mm, and the thickness of the hinge axis 54 was 8 mm; the split for swing actuators 24 was 400 mm, with the outer drive units offset by about 150 mm each from the front faces of device 1. The total weight of the bending device 1 was less than 500 kg, but it was possible to bend the sheet metal 2 mm thick without any problems.

For

Elevator Verkaufsgerate-Gesellschaft m.b.H .:

Claims (14)

Patent claims 1. A sheet bending device (1) having two pivotally interconnected bending bows (19, 20) arranged side by side and defining a sheet-bearing plane (91) at rest, at least at rest, with the touching zone (84) at rest; one is oscillatingly arranged and coupled to the oscillating actuator (24), and to the anti-holding pedestal (10), arranged linearly between the working position on the sheet (18) and the backward drawn position and standing opposite the bending pedal (19, 20), around which in the working position, the sheet (18) is bent, characterized in that the two bending bows (19, 20) are directly pivotally connected to one another in the working area with their respective edges facing each other. Apparatus according to claim 1, characterized in that the two bending bows (19, 20) are independently rotatable, the oscillating actuators (24) being preferably distributed over the width of the bending device (1) by the bending bows (19, 20), and the anti-hold pedal (10) is only linear in motion. Device according to claim 2, characterized in that the two bending bowls (19) are arranged independently of each other by oscillating actuators (24). Apparatus according to claim 2 or 3, characterized in that the anti-holding pedal (10) is pulled back in the last phase of bending the sheet (18) to allow the sheet (18) to be bent. Device according to claim 1, characterized in that one bending pedal (20) is stationary and the other bending pedal (19) as well as the anti-pedal pedal (10) are pivotally mounted, the oscillating bending pedal (19) being movable with double angular velocity compared to the anti-hold pedal (10). Device according to one of claims 1 to 5, characterized in that between e.g. a cross-sectioned, convexly curved, flattened sheet metal contact zone (84) of each bending pendulum (19, 20) and a hinged hinge joint (53) provided a recess (90) in the bending pendulum (19, 20), the hinged pivot axis (21 ) is slightly offset from the plate (91) plane. Device according to one of Claims 1 to 6, characterized in that the bending bows (19, 20) are provided with, apart from each other, the width of the bending device (1) arranged, detachable tool segments (55; 85). Device according to Claim 7, characterized in that the tool segments (55) are, by means of a simple plug-in connection (82, 83), e.g. grooves and pins, held opposite to the zones (84) of touching the sheet lying on the bending arms (19, 20), which for the rest act as tool holders. Device according to claim 7 or 8, characterized in that the tool segments (55) are pivotally interconnected, whereby the hinge joint (53) of the bending bows (19, 20) is formed by means of the hinge ties of all two tool segments. Device according to claim 9, characterized in that the tool segment pairs are provided with their own hinge axes adapted to the length of the segments (54). Device according to claim 10, characterized in that the hinge axes (54) of the tool segments project each way into the hinge ears (52) of the adjacent pair of tool segments. Device according to claim 7 or 8, characterized in that there is provided a common hinge axis (54) extending through all the tool segments (55). Apparatus according to one of Claims 1 to 12, characterized in that the bending bows (19, 20) or optionally the tool segments (55) are provided with special sheet-forming zones (84) forming pads (85). Device according to claim 13, characterized in that the inserts (85) are screwed onto the bending sockets (19,20) or tool segments (55). 16. 16. 17. 17. Apparatus according to one of Claims 1 to 14, characterized in that, as an oscillating actuator (in each case), a toothed rail (61. 62; 58) is provided, which is rigidly provided with the associated bending pedal (19, 20; 19). connected and driven through the seated stepson (63, 64: 60) on the shaft (27, 28). Device according to claim 15, characterized in that the toothed rail (61, 62) is mounted in a circular arc shaped bed, e.g. bearing groove (78), on stationary bearing portion (75) arranged on frame (2). Apparatus according to claim 15 or 16, characterized in that two separate electric motors (72, 73) are provided for the rotary drive of the two bending shafts (19, 20) of the adapted shaft (27, 28). Elevator Verkaufsgerate-Gesellschaft m.b.H. For her: 2200S. Summary A sheet bending device 1 is described with two interconnected bending blades 19, 20 arranged side by side, of which at least one is disposed and coupled to the oscillating actuator 24, and pulled between the working position on the sheet 18 and back drawn in position linearly spaced opposite to the bending jacks 19,20 standing anti-grip arms 10, around which a sheet 18 is folded in the working position, the two bending jokes 19, 20 having the edges facing each other in the working position directly facing each other connected via hinged link 53.