EP0809551B1 - Machine a plier des toles avec un dispositif de verrouillage - Google Patents

Machine a plier des toles avec un dispositif de verrouillage Download PDF

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Publication number
EP0809551B1
EP0809551B1 EP96901634A EP96901634A EP0809551B1 EP 0809551 B1 EP0809551 B1 EP 0809551B1 EP 96901634 A EP96901634 A EP 96901634A EP 96901634 A EP96901634 A EP 96901634A EP 0809551 B1 EP0809551 B1 EP 0809551B1
Authority
EP
European Patent Office
Prior art keywords
brake
bending
sheet metal
stamp
bending device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP96901634A
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German (de)
English (en)
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EP0809551A1 (fr
Inventor
Johann Kirchner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SBM Schoeller Bleckmann Medizintechnik GmbH
Original Assignee
SBM Schoeller Bleckmann Medizintechnik GmbH
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Filing date
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Application filed by SBM Schoeller Bleckmann Medizintechnik GmbH filed Critical SBM Schoeller Bleckmann Medizintechnik GmbH
Publication of EP0809551A1 publication Critical patent/EP0809551A1/fr
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Publication of EP0809551B1 publication Critical patent/EP0809551B1/fr
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Classifications

    • 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

Definitions

  • the invention relates to a sheet metal bending device according to the introductory part of claim 1.
  • a sheet metal bending device For example, from the US 3 044 526 A or W092 / 16319 A it is known in one Sheet metal bending device vertically up and down a punch to be arranged movably in a machine frame, and below of which in the machine frame two lower bending dies by one horizontal axis to be pivoted. Thereby bring with this Type of bending device the lower punch the Bending work on pivoting while the upper one Bending punch locked in the working position on the sheet or is determined and acts as a counter stamp.
  • the counter-bending punch can be locked for example via a self-locking spindle drive (W092 / 16319 A) or with a pressure cylinder drive Knee lever joint (US 3 044 526 A) are accomplished.
  • the known locking devices are in this respect of Disadvantage than for a self-locking spindle drive upper punch after a locking a release of the self-locking is often difficult again, which is why shaking or the like are required; and in the case of the impression cylinder drive with toggle joint locking in only one at a time certain working position is possible. If with others Another working position for the upper punch a complex adjustment mechanism is required be provided and activated, because that Toggle joint no locking or locking of the upper Bending punch in different vertical positions of the same enables.
  • DE 22 09 884 A also describes a cutting press, during which one of the drive movements during cutting counteracting braking force applied to the press ram becomes. It is a movement brake with which kinetic energy converted into thermal energy by sliding friction becomes.
  • the brake is actuated via a Hydraulics, at a specific point in time Work process, namely the so-called "breakthrough", as well the subsequent release of the brake, and such braking activity is typical of crank or eccentric presses like that known cutting press, but is not suitable for locking a counter-bending punch, in which a very small one Movement relative to the side stands for the bending process would be extremely disadvantageous, as this increases the distance change between the bending tools and thus the bending accuracy would worsen. It would therefore be for the present one Locking device very essential that a real "standstill brake" is present.
  • the DD 85 047 A finally shows a locking device, one with a toothed tab against one with a corresponding toothing surface of the stand of Bending machine is tightened.
  • a bolt is included Screw nut provided. It is essential that the toothing is arranged transversely to the action of force, with friction conditions does not matter.
  • the adjustment range is through the Limited tooth pitch. In the event of a change in the position of the Bending beams have to do numerous work steps become.
  • the sheet metal bending device With such a design of the sheet metal bending device it is possible to use the punch in a wide range Hold positions quickly and safely and nonetheless to release again quickly. It is in itself - for example in the case of smaller sheet metal bending devices - definitely conceivable, the brake rails on the bending punch - in particular on its longitudinal side edges parallel to the direction of movement - to be firmly attached, whereas the brake shoes together with the corresponding Drive in the area of the side guides, usually the side stand of the machine frame, movably housed can be. This can be done with regard to that in the machine frame mostly cheaper space can be quite useful. However, it is particularly preferred according to the invention if the movable Brake shoes are stored on the punch, whereas the Brake rails stationary on the side guides or side stands be attached.
  • joint rods can be used as rigid, massive levers (two-joint rods) be articulated in a bearing on the punch, the Positions of the articulation points according to the respective circumstances, but especially in the sense of being as efficient as possible Initiation of forces can be selected.
  • the Joint rods at an angle to the direction of movement of the bending die e.g. at an angle between 40 ° and 50 °, in particular 45 °, preferably 48 °, have longitudinal axis.
  • a relatively light running linkage is provided, the is coupled to the drive, and it has a particular advantage proved themselves here when to put on or move back the Brake shoes on or from the brake rails pivotable on Parallelogram linkages with double-armed levers mounted on a bending punch are provided on the one hand articulated with the Brake shoes, possibly the brake brackets, and on the other hand are connected to the drive.
  • the parts of the holding brakes on the side of the bending punch in particular the brake shoes, including the bearings, can in themselves, for example for smaller versions of sheet metal bending devices, simple be provided on one side of the punch, then due to a small lever arm (the distance from the Plane of symmetry of the counter-bending punch) acting torques can still be negligible.
  • a small lever arm the distance from the Plane of symmetry of the counter-bending punch acting torques can still be negligible.
  • a symmetrical structure i.e.
  • the counter-bending punch from a rigid box construction with two parallel, vertical plates, the tool holder as the lower one End, an upper end bar and one in between, in Inside the box, arranged locking device, which has two mirror-image brakes facing outwards Machine frame side stands work out. Every brake is there from a movable brake shoe and a fixed, on Side stand attached brake rail.
  • the brake shoe is on a brake console arranged at the end of a powerful, movable lever, the (two) hinge rod, is articulated.
  • the Brake shoes are shared by both sides acting drive via parallelogram linkage to the brake rails pressed and biased.
  • the side stands are with Help from before and after the punch, i.e.
  • the brakes are opened again ("release") by means of the brake drive, the two articulated rods Join the movement as a slight swivel movement; the upper cheek is now free and can be moved using its linear actuator become.
  • the drive of the brake contains a motor-driven, centrally arranged, vertical spindle and a plate-shaped, movable yoke that carries the spindle nut.
  • the spindle together with the drive motor is inside the top beam stored.
  • the yoke engages in the parallelogram linkage on both sides one, thus by the yoke during the up and down movement the spindle nut are taken with the lever pairs of Parallelogram linkage using rollers on the top and bottom of the yoke.
  • the parallelogram linkages are mounted on pivot pins within the upper beam and at the outer ends via spring washers with the brake brackets the brake shoes are connected in an adjustable, preloaded manner.
  • the Disc springs act in addition to the desired initial contact pressure compensation of manufacturing inaccuracies when the brake is closed between both sides.
  • the brake rails and Brake shoes engage with a congruent zigzag profile Longitudinally one into the other, the individual prongs mutually support each other against bending under load. Due to the inclination of the contact surfaces due to the zigzag profile the normal force is increased so much that the coefficient of friction the conventionally machined braking surfaces for a safe Lock is sufficient.
  • the brake rail is longer than that Brake shoe executed, which locks the punch is possible in a wide range.
  • a sheet metal bending device 1 is in shape a so-called vibration bending machine, which illustrates a general has designated with 2 machine frame to which front side stand 3, 4 belong, which with vertical Side guides 5 and 6 (see also Fig. 5) for an upper, vertically movable up and down, serve as a counterstamp Bending punch 7 are equipped.
  • This upper punch 7 is below for the sake of simplicity and for the sake of better Distinction also called counterstamp 7).
  • the counter stamp 7 consists of a rigid construction in a box executed upper cheek 8 at its upper edge with a spread over most of the machine width, i.e.
  • the counter-stamp 7 is by means of the side guides 5, 6 along the side stands 3, 4 vertically down to a working position, in which the sheet to be bent (not shown) against the lower punch 12 is clamped, and back into one upper rest position adjustable.
  • one in itself conventional linear actuator such as the one already mentioned W092 / 16319 A disclosed, provided in the area of the side stand 3, 4 his.
  • a drive and guide bar 14 with the help of a driven pinion 15, which with a toothing 16 meshes with the drive and guide bar 14, vertically movably mounted, furthermore in pairs for guidance arranged guide rollers 17 serve.
  • the drive drive shown broken off in FIG. and guide bar 14 and it is in its upper region rigidly connected to the upper cheek 8 of the counter-punch 7, see.
  • Fig. 4 in which half of the counter-stamp 7 together with the upper part of the drive and guide bar 14 is shown.
  • the drive of the pinion 15 in the area of the two side stands 3, 4 can in a conventional manner from a motor gear unit 18 (see Fig. 2) about waves not visible be derived.
  • a motor gear unit 18 see Fig. 2
  • the two side stands 3, 4 with a smaller width than below, and they are with the help of a front and a rear drawstring 19, 20 clamped together in the form of plate-shaped cross bars that overall a rigid frame construction is achieved.
  • This Drawstrings 19, 20 can be seen from the representations in FIGS. 2 and 3, and in the area of these drawstrings 19, 20 are on the Side stands 3, 4 mirrored brake rails 21 with the help rigidly fastened by bolts 22, as shown in particular in Figures 3 and 5 for the one shown in Figure 1 on the right Side stand 3 can be seen.
  • brake rails 21 are Part of a locking device for the counter-stamp 7, if this in the working position when bending the respective Blechs is located, and this locking device consists in essentially of two arranged in mirror image to each other Parking brakes 23 (see Fig. 3 and 4), each one with the associated brake rail 21 interacting brake shoe 24 contain.
  • Each brake shoe 24 is on bolts 25 on a brake console 26 attached, which in turn over a massive executed pivot pin 27 on a solid joint rod or Swivel lever 28 is pivotally attached.
  • This joint rod 28 is also massive at its other end over one executed swivel bearing 29 with the box structure of the Upper beam 8, i.e.
  • Pivot bearing 29 is located at a distance X from approximately 20% of the total machine width from the side edge of the counter stamp 7, cf. the representation in Fig.1.
  • Such Arrangement of the pivot bearing 29 at a distance from Counter margin stamp 7 margin of about 1/5 of Machine width or counter-punch length has changed with regard to a minimization of the bending due to that of the lower bending dies 12 applied bending forces and the Introduction of these forces via the pivot bearings 29 and Joint rods 28 in the brake brackets 26 and brake shoes 24 as proven particularly efficient.
  • Lever linkage that has a central motor 33 and a Angular gear 34 driven by means of a spindle drive 35 becomes.
  • the motor 33 is seated, as can be seen in FIG is, on a longitudinal beam 36, which is also the two pivot bearings 29 (only one, right, can be seen in FIG. 4) against a squeeze apart.
  • a longitudinal beam 36 which is also the two pivot bearings 29 (only one, right, can be seen in FIG. 4) against a squeeze apart.
  • an approximately rectangular recess 37 in the rear plate 31 of the upper beam 8 can be seen, which gives access to the motor 33 and to the bevel gear 34.
  • the spindle drive 35 contains an extending in an elongated housing 38 and in an upper bearing 39 rotatably mounted spindle 40 with its longitudinal axis is essentially vertical within the upper cheek 8 is arranged.
  • This spindle 40 Spindle nut 41 with a plate-shaped, horizontal Yoke 42 is firmly connected. Therefore, when the spindle 40 from the motor 33 is driven in rotation via the bevel gear 34, the Spindle nut 41 and with it the yoke 42 vertically depending on the direction of rotation the spindle 40 can be adjusted downwards or upwards.
  • This vertical adjustment movement is made on the yoke 42 via rollers 43, 44 adjacent and attached parallelogram linkage 45 with, the two-armed lever 46, 47 in the area of Yokes 42 clamped together by short connecting rods 48 are.
  • the levers 46, 47 are near the other outer ends hinged to a support block 49, and at a short distance of which these levers 46, 47 are connected to pivot pins 50, 51 Plates 30, 31 of the upper cheek 8 are pivotally mounted.
  • the support block 49 which consists of several plates or sub-blocks can be, the brake console 26 carries a plate spring package 52, which for example with the help of bolts 53 in its Preload is adjustable or adjustable. From Fig.3 and Fig. 4A is more specifically the articulated connection of the parallelogram linkage 45 with the support block 49 Swivel pin 54 can be seen.
  • the plate spring assemblies 52 cause the Brake brackets 26 with the brake shoes 24 attached to them With the help of the parallelogram linkage 45 slightly outwards (according to 4 to the right) are moved, a compensation of manufacturing tolerances and in motion control even if the respective parallelogram linkage 45 if it is moved in the middle by the spindle drive 35 to the Pivots 50, 51 pivots and thereby the joints 54 Brake console 26 with the brake shoes 24 - while pivoting the Articulated rods 28 around their pivot bearing 29 - initially against the Brake rail 21 presses resiliently (Fig. 4, 4A).
  • the brake rails 21 as well as the end faces of the brake shoes 24 are like 3 can be seen in particular in the transverse direction with provided a zigzag-shaped profile 55, so that in the longitudinal direction longitudinal direction corresponding to the vertical direction, generally V-shaped grooves or ribs are formed. Furthermore are the end faces that come into contact with each other tempered steel existing brake shoes 24 and brake rails 21 processed in a conventional manner, and through the zigzag profile 55 becomes a mutual cross support and one Increased normal force achieved when braking.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Auxiliary Devices For And Details Of Packaging Control (AREA)

Claims (15)

  1. Machine de cintrage de tôles, comportant un poinçon de cintrage (7) propre à effectuer un mouvement alternatif linéaire entre deux colonnes latérales (3, 4) dans un bâti de machine (2), et un dispositif d'arrêt pour le poinçon de cintrage (7), caractérisée par des freins de retenue (23) agissant entre le poinçon de cintrage (7) et les colonnes latérales (3, 4) pour fixer le poinçon de cintrage (7) dans la phase de cintrage au niveau des colonnes latérales (3, 4), et présentant des rails de freinage (21) et des mâchoires de frein (24) propres à être appliquées, par un dispositif d'entraínement (33, 34, 35), contre ces rails de freinage (21) et à en être écartées pour être ramenées en arrière.
  2. Machine de cintrage de tôles selon la revendication 1, caractérisée en ce que les rails de freinage (21) sont disposés au niveau des glissières latérales de guidage (5, 6), tandis que les mâchoires de frein (24) sont montées au niveau du poinçon de cintrage (7).
  3. Machine de cintrage de tôles selon la revendication 1 ou 2, caractérisée en ce que les mâchoires de frein (24) sont fixées sur des consoles de frein (26) montées de manière articulée.
  4. Machine de cintrage de tôles selon l'une des revendications 1 à 3, caractérisée en ce que les mâchoires de frein (24), le cas échéant les consoles de frein (26), sont fixées de manière articulée sur des barres articulées (28) montées par joint d'articulation au niveau du poinçon de cintrage (7).
  5. Machine de cintrage de tôles selon la revendication 4, caractérisée en ce que les barres articulées (28) présentent un axe longitudinal, qui s'étend obliquement par rapport à la direction de déplacement du poinçon de cintrage (7), par exemple selon un angle compris entre 40° et 50°, notamment un angle de 45° et, de préférence, de 48°.
  6. Machine de cintrage de tôles selon la revendication 4 ou 5, caractérisée en ce que les points d'articulation (29) des barres articulées (28) au niveau du poinçon de cintrage (7) sont chaque fois prévus à une distance (x) des bords latéraux du poinçon de cintrage (7), mesurée dans le sens longitudinal du poinçon de cintrage (7), transversalement à la direction de déplacement, et représentant approximativement 1/5ème de l'étendue longitudinale complète du poinçon de cintrage (7).
  7. Machine de cintrage de tôles selon l'une des revendications 2 à 6, caractérisée en ce que, pour appliquer les mâchoires de frein (24) contre les rails de freinage (21), ou bien pour les en éloigner, il est prévu des tiges de parallélogramme (45), formant des leviers à deux bras, qui sont montées de manière à pouvoir pivoter contre le poinçon de cintrage (7) et qui sont reliées, d'une part, de manière articulée aux mâchoires de frein (24), le cas échéant aux consoles de frein (26) et, d'autre part, au dispositif d'entraínement (33, 34, 35).
  8. Machine de cintrage de tôles selon la revendication 7, caractérisée en ce que le dispositif d'entraínement présente un arbre (40) pouvant être entraíné en rotation par un moteur (33) et monté au niveau du poinçon de cintrage (7) au milieu de l'étendue longitudinale de celui-ci, et sur lequel est placé un écrou (41) relié à une barre transversale (42), si bien que les tiges de parallélogramme (45) sont chaque fois maintenues, par exemple par l'intermédiaire de galets de roulement (43, 44), contre la face supérieure et contre la face inférieure de la barre transversale (42).
  9. Machine de cintrage de tôles selon la revendication 7 ou 8, caractérisée en ce que les tiges de parallélogramme (45) sont reliées, par l'intermédiaire de groupes de ressorts à disques (52), précontraints de manière réglable, aux mâchoires de frein (24) et, le cas échéant, aux consoles de frein (26).
  10. Machine de cintrage de tôles selon l'une des revendications 1 à 9, caractérisée en ce que les mâchoires de frein (24) et les rails de freinage (21) présentent un profil (55) qui s'étend en forme de zigzag, dans la section transversale, perpendiculairement à la direction de déplacement du poinçon de cintrage (7).
  11. Machine de cintrage de tôles selon l'une des revendications 2 à 10, caractérisée en ce que, dans la direction du déplacement du poinçon de cintrage (7), les rails de freinage (21) sont réalisés plus longs que les mâchoires de frein (24).
  12. Machine de cintrage de tôles selon l'une des revendications 1 à 11, caractérisée en ce que les deux colonnes latérales (3, 4) sont reliées l'une à l'autre par deux tirants (19, 20), par exemple en forme de plaques, disposés des deux côtés du poinçon de cintrage (7).
  13. Machine de cintrage de tôles selon l'une des revendications 1 à 12, caractérisée en ce que les mâchoires de frein (24) et les rails de freinage (21) consistent en un acier de traitement.
  14. Machine de cintrage de tôles selon l'une des revendications 2 à 13, caractérisée en ce que les mâchoires de frein (24), le cas échéant avec leurs consoles de frein (26), ainsi que leur dispositif d'entraínement (33, 34, 35) sont disposés à l'intérieur d'une cage (8), réalisée en forme de caisson, du poinçon de cintrage (7), les mâchoires de frein (24) et, le cas échéant, les consoles de frein (26) faisant saillie vers l'extérieur par des ouvertures pratiquées au niveau des bords latéraux de la cage en forme de caisson (8), et la cage (8) portant un outil de cintrage (11) par l'intermédiaire d'un porte-outil (10).
  15. Machine de cintrage de tôles selon la revendication 14, caractérisée en ce que la cage en forme de caisson (8) est conçue avec une plaque avant (30) et une plaque arrière (31) ainsi qu'avec un rebord de fermeture (9), qui est disposé au niveau du côté dirigé à l'opposé de l'outil (11) et qui laisse libre les ouvertures d'accès aux mâchoires de frein (24) et, le cas échéant, aux consoles de frein (26), le caisson de la cage (8) étant directement fermé par le porte-outil (10) au niveau du côté opposé au rebord de fermeture (9).
EP96901634A 1995-02-08 1996-02-08 Machine a plier des toles avec un dispositif de verrouillage Expired - Lifetime EP0809551B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT232/95 1995-02-08
AT23295 1995-02-08
AT23295 1995-02-08
PCT/AT1996/000022 WO1996024444A1 (fr) 1995-02-08 1996-02-08 Dispositif d'arret

Publications (2)

Publication Number Publication Date
EP0809551A1 EP0809551A1 (fr) 1997-12-03
EP0809551B1 true EP0809551B1 (fr) 2000-05-10

Family

ID=3485073

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96901634A Expired - Lifetime EP0809551B1 (fr) 1995-02-08 1996-02-08 Machine a plier des toles avec un dispositif de verrouillage

Country Status (4)

Country Link
EP (1) EP0809551B1 (fr)
AT (1) ATE192676T1 (fr)
DE (1) DE59605187D1 (fr)
WO (1) WO1996024444A1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3044526A (en) * 1960-02-15 1962-07-17 Percy L Cady Jr Brake for forming metal plate and sheet
US3282076A (en) * 1963-12-20 1966-11-01 Laval Turbine Brakes for forming plate or sheet workpieces
JPH072088Y2 (ja) * 1988-11-15 1995-01-25 株式会社小松製作所 曲げ機械の工具位置制御装置
GB2262464B (en) * 1988-12-29 1993-09-08 Amada Co Ltd Sheet workpiece bending machine
US5121626A (en) * 1991-08-06 1992-06-16 Caterpillar Inc. Adjustable die support for a press brake

Also Published As

Publication number Publication date
ATE192676T1 (de) 2000-05-15
WO1996024444A1 (fr) 1996-08-15
DE59605187D1 (de) 2000-06-15
EP0809551A1 (fr) 1997-12-03

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