EP0575393B1 - Cintreuse pour toles - Google Patents

Cintreuse pour toles Download PDF

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Publication number
EP0575393B1
EP0575393B1 EP92906012A EP92906012A EP0575393B1 EP 0575393 B1 EP0575393 B1 EP 0575393B1 EP 92906012 A EP92906012 A EP 92906012A EP 92906012 A EP92906012 A EP 92906012A EP 0575393 B1 EP0575393 B1 EP 0575393B1
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EP
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Prior art keywords
bending
sheet
punch
punches
machine according
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EP92906012A
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German (de)
English (en)
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EP0575393A1 (fr
Inventor
Otto Schubert
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Lift Verkaufsgerate-Gesellschaft Mbh
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Lift Verkaufsgerate-Gesellschaft Mbh
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Priority claimed from PCT/AT1991/000044 external-priority patent/WO1991013704A1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/04—Bending sheet metal along straight lines, e.g. to form simple curves on brakes making use of clamping means on one side of the work
    • B21D5/042—With a rotational movement of the bending blade

Definitions

  • the invention relates to e.g. Known from US-A-3 044 526, sheet metal bending device with three punches, namely two mutually pivotably connected bending dies, which are arranged next to one another and define a sheet metal contact plane with sheet metal contact zones in the rest position, and one between a working position on the sheet metal and a retracted one Position linearly movably arranged, opposite the bending punches, two stamps are pivotally arranged and each coupled to a swivel drive, and the sheet is bent by pivoting at least one of the bending punches in the working position.
  • the best known and most widespread technique for bending sheet metal or folding is to move an upper punch against the sheet resting on a lower die, the punch pressing the sheet with the area of the bending edge to be formed into the die (cf. e.g. FR-A-2 201 973, but also US-A-2 649 128), whereby the bending of the sheet is accomplished.
  • the disadvantage here is that generally no precisely defined or sharp bending edges can be formed, that only one very specific bend, that is to say a very specific bend angle, can be produced per die, and that a considerable part of the energy applied by friction on Die is lost.
  • a bending device for already profiled sheets (WO 81/02535) in order to provide these profiled sheets with a corrugation, with an upper, up and down movable die with a stationary lower die and with oblique ones arranged on both sides in the direction their main level works diagonally up and down movable additional stamps. While the upper punch forms the corrugation in the sheet with the stationary lower punch opposite it, the two oblique punches on the side prepare the next corrugation.
  • This known bending machine is not designed and is not suitable for simple bending of a sheet with the sharpest possible bending edge.
  • the swivel bearings for the two lower punches are attached to the outside of the two end faces of the bending device, the swivel drives in the form of working cylinders also being provided on these end faces.
  • the main disadvantage of this is that the bending punches have to be made extremely solid, especially when larger machine widths (e.g. 2 m or 3 m) are desired, although it is nevertheless not possible to achieve an exact bend in the sheet metal in the area of the machine center, rather the bent sheet metal in this central area is usually even more "open” than in the area of the ends, ie the bent sheet then has a curved, convex shape when viewed over the bending length.
  • the sheet metal bending device of the type mentioned is characterized in that the two bending punches are directly connected to one another along their edges facing one another in the rest position across the width of the bending device by a hinge joint connection offset from the sheet metal contact plane, with each bending punch being located between the sheet metal contact zone and the hinge joint is provided with a recess in the bending punch, and the bending punches are equipped with detachable tool segments which are arranged next to one another over the width of the bending device and which are connected in pairs by hinge joint connections, the hinge joint connection of the bending punch being formed by the hinge joint connections of all tool segment pairs .
  • the aim should be the merely linear mobility of the counterstamp, although this is not absolutely necessary, and in order to provide a possible alternative for the sheet to be bent in the aforementioned "collision" or to continue bending after bumping against the counterstamp
  • the two bending punches are assigned independent swivel drives. With the help of the independent swivel drives, it is then possible to simply stop the one punch in the event of a collision, so that on the side of this punch, where the side of the sheet with the sheet section that has already been bent is located, the sheet is then simply held, whereas the other punch is pivoted further to bend the sheet further.
  • this asymmetrical mode of operation at least a large part of the Occurring horizontal components of the bending forces compensated via the hinge joint, so that only relatively small force components are introduced into the punch and from this into the frame.
  • a kinematically the above embodiments Equivalent, preferred in terms of the formation of the stationary part of the bending device in certain cases (for example because of the stationary fixation of one sheet metal section during bending) is further characterized in that the one bending punch is stationary and the other bending punch and the counter-punch are pivotally mounted , wherein the pivotable bending punch can be driven at twice the angular speed compared to the counter-holding punch.
  • the present bending device is suitable for particularly extreme bending work according to the articulated connection specified, and it is particularly advantageous if the counter-holding stamp is provided so as to be retractable from the bending stamps in order to enable the sheet to be folded in the last phase of the bending of the sheet.
  • the bending punch is advantageously possible for the tool segments to be held by means of a mere plug-in connection, for example a tongue and groove connection, on the side opposite the sheet metal contact zones on the bending dies, which otherwise act as tool holders .
  • the tool segment pairs are provided with their own hinge axes that are adapted to the segment length.
  • the tool segment hinge axes each protrude on one side into the hinge eyelets of the adjoining tool segment pair.
  • the tool segments are provided with separate inserts which form the sheet metal contact zones.
  • the inserts can be screwed onto the tool segments.
  • a circular toothed rail is provided as the swivel drive, which is firmly connected to the associated bending punch and which is driven by a pinion seated on a shaft.
  • the toothed rail is mounted in a circular bearing, for example a bearing groove, on a stationary bearing part. In this way, the respective bending punch can be mounted on the frame of the bending device at the same time - via the toothed rails. It is also an advantage if two separate electric motors are provided for rotatingly driving the two shafts assigned to the bending dies.
  • the present sheet metal bending device, bending machine or bending press generally designated 1, as is currently particularly preferred, has a lower frame 2, on which vertical guides 5 are provided in the front main supports 3, 4, in which an upper tool holder 9 is guided vertically up and down with a cheek- or sword-shaped counter-stamp 10 (also called upper tool or simply sword).
  • This counter-stamp 10 is preferably interchangeably attached to the tool holder 9, but could also be in one piece with it;
  • a more or less cutting-like lower bending edge 13 is provided, but other cross-sectional shapes can also be provided, depending on the bend to be produced.
  • spindle drives for example, are provided for moving the upper counter-plunger 10 up and down, as is schematically illustrated at 14 in FIG. 1.
  • These spindle drives 14 contain, for example, a spindle 16 driven by an electric drive motor, possibly via a gear and a clutch (not shown), which interacts with a spindle nut 17 connected to the tool holder 9 in order to rotate the tool holder 9 with the spindle 16 when it rotates Counterstamp 10 to move up and down in the guides 5.
  • These spindle drives 14 and further drive devices to be explained in more detail are attached to the frame 2 in a conventional manner.
  • two lower, plate-shaped or cheek-shaped bending punches 19, 20 are further provided on the frame 2.
  • These two lower bending dies 19, 20 are pivotally mounted on the frame 2 in a manner to be explained below, whereby they can be pivoted about a common pivot axis 21 (see FIGS. 5 to 7) which are to be bent in the region of the bending edge 22 to be produced Sheet 18, but slightly below it, and which, in particular, also lies in the plane 23 (FIGS. 3 and 5) of the upward and downward movement of the counter-holding die 10 defined by the guides 5, 6.
  • a drive mechanism for pivoting the lower bending dies 19, 20 around the common pivot axis 21 is a pivot mechanism which, in the present exemplary embodiment, distributed over the width of the bending device 1, contains a plurality of pivot drives in the form of rack and pinion gears indicated schematically at 24 in FIGS. 1 to 3.
  • an arc-shaped toothed rack or rail 61, 62 is in each case firmly attached to the lower region of the respective lower bending die 19 or 20, as can be seen from FIGS. 1 to 3 and also from FIGS. 8 and 9.
  • These toothed racks or segments 61, 62 mesh with shafts 27 and 28, for example of the same size, which are seated on shafts 27 and 28 which are parallel to one another and to the bending dies 19, 20.
  • the two shafts 27, 28 are each driven by one - for example electrical - Drive motor 72 or 73 - possibly via a gear, not illustrated in detail - driven, as can be seen from FIG. 1.
  • the two shafts 27, 28 extend over the entire width of the bending device 1, and they are rotatably mounted on the frame 2 on the end face and also at intermediate points, in the region of the individual rack and pinion gears, in corresponding bearing parts 75, which will be explained in more detail below.
  • each rack and pinion gear 24 there is a rack 61 and 62 and a gear 63 and 64 mounted on the corresponding shaft 27 and 28 for rotation therewith, and as already mentioned above, several such rack and pinion gears 24 are provided as swivel drives distributed over the width of the bending device 1 , so that the drive torque can be distributed.
  • the toothed racks 61, 62 are therefore moved according to an arc-shaped path, the center of which lies on the pivot axis 21, pivoting the lower bending punches 19, 20 connected to them apart in the manner of a spreading apart, cf. in particular the representations in Fig. 5 (rest position) and 6 and 7 (swung apart working position).
  • bearing parts 75 For the above-indicated mounting of the shafts 27, 28 and, on the other hand, the bending dies 19, 20 on the frame 2, a plurality of bearing parts 75 extending transversely to the cross member 74 are distributed over the machine width on a fixed cross member 74 of the frame 2 at the locations of the rack and pinion gears 24 firmly attached.
  • These bearing parts 75 contain replaceable bearings 77 (see also FIGS. 2 and 3) for the shafts 27, 28 on the one hand via removable bearing covers 76, and on the other hand they are in their upper region on both sides with circular-shaped sliding grooves 78 (see FIG.
  • the two shafts 27, 28 are designed with a cross section in the form of a so-called “constant thickness", so that the pinions 63 and 64 are not weakened , as in the case of a keyway connection, to be able to take up rotation.
  • the respective bending die 19 or 20 can be accommodated with the associated toothed segment 61 or 62, for example in a simple plug-in seat or else an interference fit between seat projections 80, 81 which are in one piece with the toothed segment 61 or 62, cf. 3 and also FIGS. 8 and 9, but it can also be screwed to it.
  • the bending dies 19, 20 are designed as tool holders with separately removable, interchangeable tool segments 55, the tool segments 55 being articulated to one another in pairs via the hinge axes 54 which are matched in their length in each case.
  • These tool segments 55 are held by a simple plug-in connection, with a longitudinally extending spring 82 and a corresponding groove 83, in the bending die 19 or 20 acting as a tool holder, so that the replacement of the tool segments 55 can be accomplished particularly simply and quickly.
  • these inserts 85 for example Tungsten carbide inserts are, which are bolted to the tool segments 55 - or the bending dies 19, 20 - via bolts 86, see FIG. Fig. 8.
  • the starting or rest position of the sheet metal bending device 1 is illustrated in Fig. 5 with full lines.
  • the upper counter-holding die 10 assumes its upper rest position which is lifted from the sheet 18, and in this position a sheet 18 to be bent can be manually or mechanically fed to the bending device 1 and brought into position on it. If a sheet bending cycle is now started, the counter-holding die 10 is first moved downwards with the aid of the spindle drives 14 (FIG. 1) until it touches the sheet 18 to be bent with its edge 13, which sheet was previously brought onto the lower bending dies 19, 20. This phase, in which the sheet 18 is practically clamped between the three stamps or tools 10, 19 and 20, is also shown in FIG Counter-stamp 10 shown in dashed lines.
  • the counter-holding die 10 is advantageously locked or locked in position, for example with the aid of the spindle drives 14 (FIG. 1), so that it forms a stationary counter-holder during this bending process.
  • the sheet 18 is bent, for example, by approximately 90 ° along the bending edge 22, cf. the representation in Fig. 6; As is further illustrated in FIG. 7, an acute bending angle can also be brought about in the sheet 18 in this bending process. If the sheet 18 had already been subjected to a bending process, see. the already bent edge 34 in FIGS. 5 to 7, so-called "collision" can occur, in which this already bent edge 34 abuts the counter-punch 10 during bending.
  • the upper counter-holding die 10 could, for example, be pivotably mounted about a horizontal axis, so that it could deflect when the edge 34 abuts.
  • the upper counter-holding die 10 could, for example, be pivotably mounted about a horizontal axis, so that it could deflect when the edge 34 abuts.
  • another solution can be provided for this collision case, with the advantage that a force equalization takes place via the hinge joint 53; Therefore, in addition to the described procedure, in which the lower bending dies 19, 20 in opposite directions and are driven symmetrically, in particular with the same angular velocity, and asymmetrical working methods are also permitted, since overall only a relatively small resulting horizontal component remains.
  • independent swivel drives are preferably assigned to the two bending dies 19, 20 in the present sheet metal bending device 1, in the present exemplary embodiment by the separate drive motors 72, 73 and the shafts 27, 28 driven by them. Therefore, in the described collision, if the sheet edge 34 against pushes the counterstamp 10 laterally, see. 7, the bending punch 20 located on this side is stopped, and then only the other bending punch 19 is pivoted further in order to complete the bending process on the cup 18, as illustrated in FIG. 7.
  • the counter-punch 10 can be moved upward out of the sheet-metal profile 18, after which the two bending punches 19, 20 are pivoted further upwards in the sense of spreading apart, as a result of which in the region of the bending edge produced 22 a fold would be generated, ie the sheet edge on the left in FIG. 7 would then be applied directly to the remaining sheet 18.
  • the frictional forces applied to the sheet metal via the contact zones 84 are sufficient to hold the sheet 18, which has already been largely bent, between the bending dies 19, 20, without the need for the counter-holding die 10.
  • the sheet metal contact zones 84 described which in the rest position of the bending dies 19, 20 (FIG. 5) are connected to or Define the support level 91 for the sheet metal 18, pass into the hinge joint 53 via a recess 90.
  • these recesses 90 create space for the sheet 18 in the region of the bending edge 22 to be produced, so that the sheet 18 is not squeezed there, as could be the case with flat, adjacent bending punches on the upper side. 5 that the hinge axis or pivot axis 21 runs somewhat below the sheet-metal contact plane 91 defined by the contact zones 84 (this is the underside of the sheet 18 in FIG. 5), which means that bending work begins Favorable lever arm for the transmission of bending moment on the sheet 18 is created.
  • the various drives for the punches 10, 19, 20 are reversed again in order to pivot the lower bending punches 19, 20 back into the vertical starting position according to FIG. 5 and to move the upper counter-holding punch 10 upward (unless this has already been done) is).
  • the bent sheet 18 can now be brought into the next bending position or removed from the bending device 1.
  • FIG. 10 to 13 is a very schematic illustration of a further sheet metal bending device 1 with its essential working parts, which fully corresponds to the exemplary embodiment described above with regard to the relative movement of its punches or tools 10, 19 and 20, but not the upper counter-punch 10 during the bending process 10 to 13 right lower bending punch 20, whereas the other lower bending punch 19 is pivoted when bending the sheet 18 (see FIGS. 11 to 13) according to the previous exemplary embodiments, and for In order to bring about the relative pivoting movements between the stamps, the upper counter-holding stamp 10 is preferably pivoted - preferably at half the angular speed in comparison to the lower left bending stamp 19, see also the intermediate position of the three stamps shown in FIG. 12 and the one in FIG 13 end position shown.
  • FIGS. 10 to 13 If one were to observe the movement sequence from the upper counter-punch 10 (rest position) in this embodiment according to FIGS. 10 to 13, a swivel movement sequence would result similar to that as explained above with reference to FIGS. 1 to 9.
  • the individual movement phases are shown in FIGS. 10 to 13, however, observed from the stationary frame (which is not illustrated in FIGS. 10 to 13).
  • Such kinematics, as in the bending device according to FIGS. 10 to 13 may be desirable if only a slight movement, if any, is to take place on the one side of the bending edge in the sheet 18 to be bent.
  • the two lower bending punches 19, 20 are in turn hinged together with interlocking eyelet members 52 to form the hinge joint 53, a hinge axis 54 extending through the entire joint arrangement.
  • the two bending dies 19, 20 To the side of the hinge joint 53, the two bending dies 19, 20 have a rounded cheek shape where they come into contact with the sheet 18 to be bent.
  • the two bending punches 19, 20 are also constructed, with a view to easier interchangeability, with individual tool segments 55, which are firmly connected to a tool carrier or lower punch part 56, for example with the aid of bolts 57.
  • the drive for these gearwheels 60 can take place in the manner already mentioned with reference to FIGS. 1 to 9 via a drive motor (not shown in more detail in FIG. 10) and a transmission.
  • Fig. 10 is also schematically illustrated with dashed lines, as when turning the gear 60 in Counter-clockwise (see arrow) the left stamp 19 is pivoted outwards, ie away from the right stamp 20.
  • the upper punch 10 as mentioned preferably at half the angular velocity in relation to the lower punch 19 — also pivots.
  • the upper punch 10 can be driven in a manner which is in principle analogous to that for the lower punch 19, the preferred transmission ratio of 2: 1 being ensured by means of a gear.
  • Such a drive arrangement is conventional per se, so that it does not need to be explained further at this point.
  • the mounting of the upper punch 10 in the frame (not illustrated in more detail) in the bending device according to FIG. 10 can in principle be provided in a manner similar to that explained above with reference to FIG. 1, i.e. in particular with front main beams 3, 4, which, however, here e.g. together with the spindle drives (14 in FIG. 1) or comparable drives would be pivotably mounted on the lower frame 2, which can be done in a manner known per se to the person skilled in the art.
  • FIGS. 11 to 13 also illustrate the pivot axis 21 for the relative pivoting between the lower bending dies 19, 20, which coincides here with the geometric axis of the joint axis 54 (FIG. 10) of the hinge joint 53.
  • the upper punch 10 is also pivoted about this pivot axis 21 during bending, see the illustration in FIGS. 12 and 13.
  • the center of the arc-shaped rails 58 lies on this pivot axis 21 (i.e. the geometric axis of the hinge joint axis 54).
  • Corresponding electrical control circuits can be provided for the drive motors, for example the drive motors 72, 73 for pivoting the bending dies 19, 20 and the drive motor (s) for the two spindle drives 14, in order to be able to switch these drive motors on and off as required.
  • hydraulic motors or pressure medium cylinders can of course also be provided instead of these electric drive motors.
  • the machine width was 1500 mm
  • the length of the tool segments 55 was 125 mm
  • the thickness of the hinge axis 54 was 8 mm
  • the division for the swivel drives 24 was 400 mm, the outer drive units each being offset by approximately 150 mm from the end faces of the device 1.
  • the total mass of the bending device 1 was less than 500 kg, and 2 mm thick sheets could be bent without any problems.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)

Abstract

Il est décrit une cintreuse pour tôles (1) comportant deux poinçons à cintrer (19, 20) reliés entre eux de manière pivotante et disposés l'un à côté de l'autre, dont au moins un est disposé de manière pivotante et couplé à un entraînement pivotant (24), ainsi qu'un contre-poinçon (10) linéairement mobile entre une position de travail sur la tôle (18) et une position de retrait et opposé aux poinçons à cintrer (19, 20). Dans la position de travail, la tôle (18) est pliée autour du contre-poinçon, les deux poinçons à cintrer (19, 20) étant reliés entre eux directement dans le champ de travail par l'intermédiaire d'une articulation à charnière (53) le long de leurs bords se faisant face dans la position de repos.

Claims (13)

  1. Cintreuse à tôles (1) comportant trois pinçons (19, 20, 10), à savoir deux pinçons de cintrage (19, 20) reliés l'un à l'autre d'une manière pivotante, lesquels pinçons de cintrage sont disposés l'un à côté de l'autre en définissant, dans la position de repos, un plan de portée de tôle (91) avec des zones de contact de tôle (84), et un contre-pinçon (10) disposé à être mobile linéairement entre une position d'opération sur la tôle (18) et une position retirée et opposé les pinçons de cintrage (19, 20), deux pinçons (19, 20; 10, 19) étant agencés d'une manière pivotante et attelés chacun à un mécanism de pivotement (24), cependant que la tôle (18) est cintrée autour du contre-pinçon (10) dans la position d'opération par pivotement d'un au moins des pinçons de cintrage (19, 20), caractérisée en ce que les deux pinçons de cintrage (19, 20) sont interconnectés directement, le long de leurs bords faisant face dans la position de repos, sur la largeur de la cintreuse (1) au moyen d'une articulation à charnière (53) décalée du plan de portée de tôle (91), cependant qu'une échancrure (90) est prévue dans le pinçon de cintrage (19, 20) entre la zone de contact de tôle (84) de chaque pinçon de cintrage (19, 20) et l'articulation à charnière (53), et en que les pinçons de cintrage (19, 20) sont equipés de segments d'outil (55) amovibles disposé l'un à côté de l'autre sur la largeur de la cintreuse (1), lesquels segments d'outil sont reliés en paires au moyen d'articulations à charnière, ladite articulation à charnière (53) des pinçons de cintrage (19, 20) étant formées par les articulations à charnière de toutes les paires de segments d'outil.
  2. Cintreuse selon la revendication 1, caractérisée en ce que plusieurs de mécanisms de pivotement (24) agissent sur chacun des deux pinçons de cintrage (19, 20) pivotants indépemment, d'une manière distribuée sur la largeur de la cintreuse (1), et le contre-pinçon n'est mobile qu'en sens linéaire.
  3. Cintreuse selon la revendication 2, caractérisée en ce que le contre-pinçon (10) est agencé d'une manière susceptible d'être retiré des pinçons de cintrage (19, 20) en vue de permettre l'agrafage de la tôle (18) dans la dernière phase de cintrage de la tôle (18).
  4. Cintreuse selon la revendication 1, caractérisée en ce que l'un (20) des pinçons est agencé de façon fixe et l'autre (19) des pinçons ainsi que le contre-pincon (10) sont montés de manière pivotante, le pinçon pivotant (19) étant susceptible d'être entrainé à la vitesse angulaire double en comparaison du contre-pinçon (10).
  5. Cintreuse selon l'une des revendications 1 à 4, caractérisée en ce que les segments d'outil (55) sont maintenus sur les pinçons de cintrage (19, 20) qui, en plus, fonctionnent en tant que portes-outil, sur la côté en regard des zones de contact de tôle (84) au moyen d'une connection mâle-femelle simple (82, 83), par exemple au moyen d'un assemblage à rainure et languette.
  6. Cintreuse selon l'une des revendications 1 à 5, caractérisée en ce que les paires de segment d'outil sont pourvues de propres axes de charnière (54) adaptés à la longeur du segment.
  7. Cintreuse selon la revendication 6, caractérisée en ce que les axes de charnière des segment d'outil (54), sur une côté, chacun se projètent dans les yeux de charnière (52) de la paire de segment d'outil consecutive.
  8. Cintreuse selon l'une des revendications 1 à 5, caractérisée en ce qu'un axe de charnière continu commun (54) est prévue, s
    Figure imgb0001
    etendant à travers tous les segments d'outil (55).
  9. Cintreuse selon l'une des revendications 1 à 8, caractérisée en ce que les segments d'outil sont pourvus d'inserts séparés (85) formant les zones de contact de tôle (84).
  10. Cintreuse selon la revendication 9, caractérisée en ce que les inserts (85) sont vissés sur les segments d'outil (55).
  11. Cintreuse selon l'une des revendications 1 à 10, caractérisée en ce qu'une crémaillère en forme d'arc de cercle (61, 62; 58) est respectivement prévue en tant que mécanism de pivotement, ladite crémaillère étant solidaire du pinçon de cintrage correspondant et entrainée par l'intermédiaire d'un pignon (63, 64; 60) cale sur un arbre (27, 28).
  12. Cintreuse selon la revendication 11, caractérisée en ce la crémaillère (61, 62) est montée dans un palier en forme d'arc de cercle, par example dans une rainure de palier (78), sur un élément fixe de palier (75) agencé sur le bâti (2).
  13. Cintreuse selon la revendication 11 ou 12, caractérisée en ce deux moteurs électriques séparés (72, 73) sont prévus pour l
    Figure imgb0002
    entraînement rotatif des deux arbres (27, 28) conjugués aux pinçons de cintrage (19, 20).
EP92906012A 1991-03-14 1992-03-11 Cintreuse pour toles Expired - Lifetime EP0575393B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
PCT/AT1991/000044 WO1991013704A1 (fr) 1990-03-15 1991-03-14 Dispositif de pliage des toles
WOPCT/AT91/00044 1991-03-14
AT1878/91 1991-09-18
AT187891 1991-09-18
PCT/AT1992/000032 WO1992016319A1 (fr) 1991-03-14 1992-03-11 Cintreuse pour toles

Publications (2)

Publication Number Publication Date
EP0575393A1 EP0575393A1 (fr) 1993-12-29
EP0575393B1 true EP0575393B1 (fr) 1994-12-07

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EP92906012A Expired - Lifetime EP0575393B1 (fr) 1991-03-14 1992-03-11 Cintreuse pour toles

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EP (1) EP0575393B1 (fr)
JP (1) JP2672402B2 (fr)
KR (1) KR960007488B1 (fr)
CN (1) CN1045731C (fr)
AR (1) AR246448A1 (fr)
AT (1) ATE115014T1 (fr)
AU (1) AU657312B2 (fr)
BR (1) BR9205777A (fr)
CA (1) CA2105587A1 (fr)
CZ (1) CZ283115B6 (fr)
DE (1) DE59200920D1 (fr)
DK (1) DK0575393T3 (fr)
ES (1) ES2065177T3 (fr)
HU (1) HU215986B (fr)
SK (1) SK279575B6 (fr)
WO (1) WO1992016319A1 (fr)

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DE102019008118A1 (de) * 2019-11-21 2021-05-27 Wolfram Hochstrate Schwenkbiegemaschine insbesondere zum Gegenbiegen mit einer Duplex-Biegewange

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CN102430617B (zh) * 2011-11-03 2014-11-05 湖北三江航天万山特种车辆有限公司 钣金大圆角加工装置
KR101533739B1 (ko) * 2015-01-22 2015-07-03 주식회사 일우산업기계 다기능 절곡 장치
CN106216448B (zh) * 2016-08-05 2018-01-09 乐清市敏捷机械有限公司 液压泵站油箱侧板的折弯加工方法
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CN111014366A (zh) * 2020-03-09 2020-04-17 山东炎黄工业设计有限公司 一种薄板折弯装置及其使用方法
CN113000716B (zh) * 2021-02-22 2023-02-24 中车青岛四方机车车辆股份有限公司 一种脱模装置及具有其的压力机
CN113441956B (zh) * 2021-07-20 2023-10-10 玖科智造(武汉)精密机械有限公司 一种建筑工程用型材切割设备
CN113333522A (zh) * 2021-08-09 2021-09-03 新沂市振港金属制品有限公司 一种金属加工连续冲压装置
CN113617890A (zh) * 2021-09-09 2021-11-09 安徽华汇电力设备有限公司 一种配电柜用不锈钢板材折弯设备
CN115502250B (zh) * 2022-09-26 2023-04-14 广东百能家居有限公司 一种不锈钢柜板的自动折弯装置及方法

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Publication number Priority date Publication date Assignee Title
DE102017006218A1 (de) 2017-06-28 2019-01-03 Technische Universität Dortmund Vorrichtung und Verfahren zum Biegen von blechartigen Werkstücken bei gleichzeitiger Druckspannungsüberlagerung
EP3424606A1 (fr) 2017-06-28 2019-01-09 Technische Universität Dortmund Dispositif et procédé de pliage des pièces à usiner en forme de tôle à superposition de contrainte de compression simultanée
DE102019008118A1 (de) * 2019-11-21 2021-05-27 Wolfram Hochstrate Schwenkbiegemaschine insbesondere zum Gegenbiegen mit einer Duplex-Biegewange
DE102019008118B4 (de) 2019-11-21 2022-09-15 Wolfram Hochstrate Schwenkbiegemaschine insbesondere zum Gegenbiegen mit einer Duplex-Biegewange

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CN1045731C (zh) 1999-10-20
JP2672402B2 (ja) 1997-11-05
SK279575B6 (sk) 1999-01-11
HU9302585D0 (en) 1993-12-28
WO1992016319A1 (fr) 1992-10-01
JPH06505677A (ja) 1994-06-30
HUT64492A (en) 1994-01-28
BR9205777A (pt) 1994-04-26
AU657312B2 (en) 1995-03-09
AU1349192A (en) 1992-10-21
DE59200920D1 (de) 1995-01-19
ATE115014T1 (de) 1994-12-15
DK0575393T3 (da) 1995-05-01
HU215986B (hu) 1999-03-29
ES2065177T3 (es) 1995-02-01
CN1064632A (zh) 1992-09-23
CZ186093A3 (en) 1994-03-16
CA2105587A1 (fr) 1992-09-15
CZ283115B6 (cs) 1998-01-14
EP0575393A1 (fr) 1993-12-29
KR960007488B1 (ko) 1996-06-05
AR246448A1 (es) 1994-08-31
SK98193A3 (en) 1994-01-12

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