EP2210680B1 - Presse plieuse dotée d'une poutre d'entraînement et d'une poutre plieuse couplée élastiquement - Google Patents

Presse plieuse dotée d'une poutre d'entraînement et d'une poutre plieuse couplée élastiquement Download PDF

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Publication number
EP2210680B1
EP2210680B1 EP10000736.8A EP10000736A EP2210680B1 EP 2210680 B1 EP2210680 B1 EP 2210680B1 EP 10000736 A EP10000736 A EP 10000736A EP 2210680 B1 EP2210680 B1 EP 2210680B1
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EP
European Patent Office
Prior art keywords
bending
press
driving
contact surface
length
Prior art date
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Active
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EP10000736.8A
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German (de)
English (en)
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EP2210680A2 (fr
EP2210680A3 (fr
Inventor
Josef Gaggl
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.)
Trumpf Maschinen Austria GmbH and Co KG
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Trumpf Maschinen Austria GmbH and Co KG
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Publication of EP2210680A3 publication Critical patent/EP2210680A3/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
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/06—Platens or press rams
    • B30B15/068—Drive connections, e.g. pivotal

Definitions

  • the invention relates to a bending press as described in the preamble of claim 1 and a method as described in the preamble of claim 14.
  • a press with a vertically movable upper cheek relative to a fixed lower cheek is known.
  • the upper beam is divided approximately in two perpendicular to a direction of force action, the two cheek parts meet in the center of the cheek and are separated from one another on both sides of the joint by a gap with a gap width that increases continuously up to the cheek ends.
  • This division of the upper beam makes it possible to achieve that the upper beam and the lower beam bend in the same direction under load at the work site and the deflection lines run at least approximately parallel.
  • the two cheek parts of the upper cheek are preferably connected to one another by coupling members at their outer end regions, these coupling members being connected to the cheek parts via hinge axes and having spring elements, whereby a stable, neutral position is ensured in the unloaded state of the cheek part receiving the bending tool.
  • Each of the two press beams comprises two outer beams arranged in parallel at a distance from one another and one inner beam each arranged between them.
  • the opposing inner bars form support surfaces for bending tools on opposite end faces.
  • These inner bars, which can be equipped with the tools, are each movable with respect to the outer bar and are coupled via resilient coupling elements, whereby a basic positioning of the bars of the bar structure is achieved.
  • a relative movement of the inner beam parts with respect to the respective outer beam parts is made possible as a function of a load applied by the pressing forces.
  • the deflection of the beams that occurs under load can be coordinated with one another and thus the immersion depth of the interacting bending tools required for an exact bending angle is kept constant over the entirety of the bending length.
  • the object of the invention is to create a press with a two-part press beam with which the force required for a bending process can be brought into alignment with a line of action of a reaction force acting on the press beam, depending on the positioning of the tools in the longitudinal direction of the press beam.
  • This object of the invention is achieved by the features recited in the characterizing part of claim 1.
  • the surprising advantage here is that during the forming process, deviations in the penetration depth of the bending tools in relation to the bending length, caused by bending of the press and table beams depending on the position of the tools, are compensated for by correcting the position of the part of the press beam that acts as a bending beam and so that a high angular accuracy is achieved on the workpiece.
  • an embodiment according to claim 2 is also advantageous, because it results in a change in the position of the drive beam relative to the bending beam by selecting appropriate adjustment paths for the drive means.
  • the drive bar and the bending bar have mutually facing contact surfaces extending over a length of the drive bar, a direct force transmission between the drive bar and the bending bar is achieved.
  • designs according to claims 3 to 5 are also advantageous because, depending on the relative position of the drive beam, the position of the force introduction into the bending beam is variable over its length to adapt to a planned position of the bending tools.
  • An embodiment according to claim 6 is possible, as a result of which the required pivotability for adapting the position of the force transmission between the drive beam and the bending beam to the intended position of the bending tools is reduced.
  • an embodiment according to claim 10 is also advantageous because it also saves components and a preload for play-free contact of the contact surfaces of the drive beam and the bending beam is achieved.
  • the object of the invention is also achieved by a method according to the measures according to claim 14.
  • the advantage is that an approximately symmetrical deflection under load of the table beam and the bending beam is achieved whereby angular errors on the work part are largely avoided and readjustments of the adjustment paths of the drive means are not necessary in many cases.
  • measures as described in claim 15 are also advantageous, because by shifting the line of action of the deformation force and thus a force introduction point on the bending beam, the deformation effect during a correction deformation stroke from a central position, based on the bending length, into an eccentric, a post-forming of the workpiece is adjusted in particular the area to be subjected to and thus the forming quality is increased.
  • All information on value ranges in the present description should be understood to include any and all sub-areas, e.g. the information 1 to 10 should be understood to include all sub-areas, starting from the lower limit 1 and the upper limit 10 , ie all subranges begin with a lower limit of 1 or greater and end at an upper limit of 10 or less, for example 1 to 1.7, or 3.2 to 8.1 or 5.5 to 10.
  • a bending press 1 in particular a press brake 2, for producing work parts 3, between bending tools 4 that are adjustable relative to one another, is shown.
  • a machine frame 5 of the bending press 1 consists, for example, of a base plate 6 on which side walls 7, 8 are arranged, projecting vertically, spaced from one another and aligned parallel to one another. These are preferably connected by a massive cross bracing 9, formed for example from a sheet metal part, at their end regions spaced from the base plate 6.
  • the side cheeks 7, 8 are approximately C-shaped to form a free space for the reshaping of the workpiece 3, a fixed table beam 12 standing on the base plate 6 being attached to the front end surfaces 10 of legs 11 of the side cheeks 7, 8 close to the floor.
  • Linear guide arrangements 15 for a press beam 16 which can be adjusted relative to the table beam 12 are provided on legs 14 of the side cheeks 7, 8 that are remote from the base plate 6.
  • the press beam 16 can be adjusted via two drive means 17, 18 of the drive arrangement 19, which are spaced apart from one another, according to double arrow 20.
  • the reshaping and forming of the workpiece 3 is carried out between the bending tools 4 arranged on opposite support surfaces 21, 22 of the press beam 16 and the table beam 12 during an adjustment stroke of the press beam 16.
  • the drive arrangement 19 is a hydraulic drive with hydraulic cylinders 23 acted on from both sides as the drive means 17, 18, with piston rods 24 being connected to the press beam 16 via spherical cap bearings 25 with the press beam 16, whereby a pivoting movement of the press beam 15 in a restricted area , by different adjustment paths of the drive means 17, 18, in one to one Front surface of the press beam 16 parallel plane is made possible and thus an immersion depth of the bending tools 4 can be influenced.
  • the hydraulic cylinders 23 are fastened to the cross bracing 9 with housings 26.
  • the housings 26 are fastened directly to the side walls 7, 8.
  • the press beam 16 is designed in two parts and consists of a drive beam 27 which is drive-connected to the piston rods 24 via the spherical cap bearings 25.
  • the drive bar 27 protrudes into a slot-shaped receptacle 29, which extends over an entire length 28 of the press bar 16, of a bending bar 30 equipped with the bending tool 4, which is adjustably mounted in the linear guide arrangements 15 for vertical adjustment, whereby an adjustment of the bending tools 4 receiving support surfaces 21, 22 of the table beam 12 and of the bending beam 30 in planes 31, 32 aligned parallel to one another.
  • the drive beam 27 and the bending beam 30 have in the slot-shaped receptacle 29 facing contact surfaces 33, 34, the contact surface 33 of the drive beam 27 extending in an arcuate manner in the direction of the length 28, whereas the contact surface 34 of the bending beam 30 in the receptacle 29 is straight and runs in a plane 35 parallel to the plane 31 of the support surface 21 of the bending beam 30.
  • Via an elastic coupling element 36 which is arranged approximately in the middle of the length 28 and connects the drive beam 27 to the bending beam 30 - which will be discussed in more detail later - a play-free contact between the contact surfaces 33, 34 of the drive beam 27 and the bending beam 30 is possible in FIG the slot-shaped receptacle 29 guaranteed.
  • the coupling element 36 is formed by a spring assembly 37 in openings 38, 39 of the drive beam 27 and the bending beam 30, the spring force caused by the spring assembly 37 being greater than the dead weight of the bending beam 30 plus the occurring Acceleration forces that occur during an adjustment movement of the press beam 16 into an upper end position.
  • the drive beam 27 protrudes into the slot-shaped receptacle 29 of the bending beam 30, the contact surface 34 extending in the plane 35 and the curved contact surface 33 of the drive beam 27 facing it touching one another in a linear manner.
  • the opening 38 crossing this is arranged in a rectangular shape.
  • the rectangular opening 39 is also arranged in the drive beam 27 and crossing it.
  • a vertically measured distance 43 of the opening 38 is smaller than a distance 44 of the opening 39 in the drive beam 27, in relation to an apex 45 of the contact surface 33.
  • the openings 38, 39 and extending over a thickness 46 of the bending beam 30, an upper and a lower pressure plate 47, 48 are arranged, which bring about the preload in the openings 38, 39 via the spiral compression spring 40 arranged between them and thus the play-free contact of the contact surfaces 33, 34 between the drive beam 27 and the bending beam 30 in the receptacle 29 is achieved.
  • the bending press 1 is shown with the two-part press beam 16, consisting of the drive beam 27 frictionally coupled to the drive arrangement 19 and the bending beam 30 adjustable in the guide arrangements 15 - according to arrow 50 - and the method according to the invention is explained in the following description.
  • the assembly of the bending press 1 with the bending tools 4 in the bending beam 30 and the table beam 12 shows an eccentric arrangement of the bending tools 4 as is often chosen when, for example, several sets of tools are used for different bending processes over the length 28 of the bending beam 30.
  • Such assembly means different force application at the force introduction points, for example the spherical ball bearings 25 and an asymmetrical design of the deflection that occurs during the bending process on the bending beam 30 and table beam 12, with conventional bending presses with one-piece press beams then leading to bending inaccuracies because the depth of immersion of the Bending tools 4 turn out differently in the case of an eccentric arrangement and thus lead to inaccuracies in an adjustment path which is predetermined for a certain bending angle and which is measured and controlled.
  • an inclined position of the drive beam 27, which connects the elastic coupling element 36 enables the line of force 49 to transfer the pressure force between the drive beam 27 and the bending beam 30 in the direction of the length 28 and thus for the forming process of the workpiece 3, due to the eccentricity of the assembly with the bending tools 4 occurring reaction force, according to - arrow 50 - in brought aligned agreement.
  • the pivoting of the drive beam 27 takes place through different adjustments of the drive means, whereby, as shown, the pin bearings 25 assume a correspondingly different position and a pivoted position of the drive beam 27 is achieved.
  • the maximum inclination of the drive beam 27 from its horizontal neutral position is once a segment height 51 of the curved contact surface 33, the segment height 51 being selected as a function of the respective length 28 of the drive beam 27.
  • segment height 51 being selected as a function of the respective length 28 of the drive beam 27.
  • FIG. 5 an embodiment of the coupling element 36 between the drive beam 27 and the bending beam 30 is shown, which is formed from at least one pressure-elastic plastic pad 52, which ensures the play-free contact of the contact surfaces 33, 34, regardless of the position of the drive beam 27, as well as the relative movement between the drive beam 27 and the bending beam 30 during a pivoting movement of the drive beam 27.
  • the bending press 1 according to the invention with the two-part press beam 16 enables, as already partially described previously, the force introduction point on the bending beam 30 by pivoting the drive beam 27 by means of appropriately preselected adjustment paths of the drive means 17, 18 in an aligned position with the force line 49 of the for a forming process on the Work part 3 to be applied force to bring.
  • a data memory e.g. position of the tool sets or an assembly diagram of the bending press 1, with one or more bending stations from cooperating bending tools, the bending length, the work part data, the Geometry of the drive beam 27 etc.
  • the forming process takes place by adjusting the drive beam 27 in the pivoted position by the same adjustment path of the drive means and thus the adjustment of the bending beam 30 takes place by the adjustment path required for a predetermined deformation, e.g. bending angle, to achieve a for the bending angle required immersion depth of the bending tools.
  • a predetermined deformation e.g. bending angle
  • the exemplary embodiments show possible design variants of the bending press 1, whereby it should be noted at this point that the invention is not limited to the specifically shown design variants of the same, but rather various combinations of the individual design variants with one another are possible and this possible variation is based on the teaching on technical action The present invention is within the ability of those skilled in this technical field. All conceivable design variants that are possible through combinations of individual details of the embodiment variants shown and described are therefore also included in the scope of protection of the appended claims.

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

Claims (15)

  1. Presse de cintrage (1), plus particulièrement presse plieuse (2), avec un châssis de machine (5), avec des joues latérales (7, 8) et une barre de table (12) fixe écartant les joues latérales (7, 8) et avec une barre de presse (16) réglable par rapport à la barre de table (12), dans des dispositions de guidage linéaires (15) du châssis de machine (5), avec une disposition d'entraînement (19) constituée d'au moins deux moyens d'entraînement (17, 18) distants entre eux,
    - dans laquelle la barre de presse (16) est constitué d'une barre d'entraînement (27) reliée en entraînement avec les moyens d'entraînement (17, 18)
    - et d'une barre de cintrage (30) reliée en mouvement avec celle-ci par l'intermédiaire d'au moins un élément de couplage élastique (36), caractérisée en ce que
    - la barre de cintrage (30) comprend un logement en forme de fente (29) s'étendant sur toute la longueur (28) de la barre de presse (16),
    - et la barre d'entraînement (27) dépasse dans ce logement en forme de fente (29),
    - dans laquelle la barre d'entraînement (27) et la barre de cintrage (30) dans le logement en forme de fente (29) comprennent des surfaces de contact (33, 34) orientées l'une vers l'autre,
    - dans laquelle la surface de contact (34) de la barre de cintrage (30) est en ligne droite et s'étend dans un plan (35) parallèle à un plan (31) d'une surface d'appui (21) de la barre de cintrage (30)
    - et dans laquelle la surface de contact (33) de la barre d'entraînement (27) s'étendant de manière incurvée en arc de cercle dans la direction de la longueur (28) de la barre d'entraînement (27).
  2. Presse de cintrage (1) selon la revendication 1, caractérisée en ce que la barre d'entraînement (27) est reliée de manière pivotante avec la barre de cintrage (30) par l'intermédiaire de l'élément de couplage (36).
  3. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce que la surface de contact (33) de la barre d'entraînement (27) est incurvée de manière convexe.
  4. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce que la surface de contact (33) de la barre d'entraînement (27) est incurvée en forme d'arc de cercle.
  5. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce que la disposition d'entraînement (19) avec les moyens d'entraînement (17, 18) est conçue pour une course de réglage au choix identique ou différente pour chaque moyen d'entraînement (17, 18).
  6. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce qu'une hauteur de segment (51) de la surface de contact (33), mesurée au milieu de la longueur (28) de la barre d'entraînement (27) est d'environ entre 0,2 % et 2,0 % de la longueur (28) de la barre d'entraînement (27).
  7. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce que la barre d'entraînement (27) et la barre de cintrage (30) sont conçues de façon à se superposer dans la direction de réglage avec des parties de parois.
  8. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce qu'une surface de base du logement (29) constitue la surface de contact (34) de la barre de cintrage (30).
  9. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce que la surface de contact (34) de la barre de cintrage (30) s'étend dans un plan parallèle à la surface d'appui de l'outil (22).
  10. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce que l'élément de couplage (36) est disposé environ au milieu de la longueur (28) de la barre d'entraînement (27) dans les passages (38, 39) traversant la barre d'entraînement (27) et la barre de cintrage (30).
  11. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce que l'élément de couplage (36) est constitué d'au moins un bloc-ressort (37) comprenant un ressort de compression en spirale (40).
  12. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce que l'élément de couplage (36) est constitué d'au moins un élément de ressort hydraulique.
  13. Presse de cintrage (1) selon l'une des revendications précédentes, caractérisée en ce que l'élément de couplage (36) est constitué d'au moins un coussin de pression en matière plastique traversant les passages (38, 39).
  14. Procédé de fonctionnement d'une presse de cintrage (1), plus particulièrement d'une presse plieuse (2), avec un châssis de machine (5), avec des joues latérales (7, 8) et une barre de table (12) fixe écartant les joues latérales (7, 8) et avec une barre de presse (16) réglable par rapport à la barre de table (12), dans des dispositions de guidage linéaires (15) du châssis de machine (5), avec une disposition d'entraînement (19) constituée d'au moins deux moyens d'entraînement (17, 18) distants entre eux, dans laquelle la barre de presse (16) est constituée d'une barre d'entraînement (27) reliée en entraînement avec les moyens d'entraînement (17, 18) et d'une barre de cintrage (30) reliée en mouvement avec celle-ci par l'intermédiaire d'au moins un élément de couplage élastique (36), caractérisé en ce que la barre d'entraînement (27) et la barre de cintrage (30) comprennent des surfaces de contact (33, 34) orientées l'une vers l'autre et s'étendant sur une longueur (28) de la barre d'entraînement (27) et en ce que, au début d'un processus de formage, à partir d'un programme de travail, la position prédéterminée de l'ensemble d'outils de cintrage correspondant est appelée à partir d'une coordonnée de longueur 0 de la barre de table (12), qui est définie par une ligne d'action de force d'un parmi plusieurs moyens d'entraînement (17, 18) pour l'application d'une force de pression sur la barre de cintrage (30) puis, en fonction de la géométrie de la barre d'entraînement (27), dans un ordinateur d'un dispositif de contrôle et de régulation de la presse de cintrage (1), une position angulaire est déterminée pour la barre d'entraînement (27) et cette position angulaire est réglée par le contrôle des moyens d'entraînement (17, 18) pour une course de réglage d'au moins un des moyens d'entraînement (17, 18), pour laquelle une position de la surface de contact (33), incurvée en forme d'arc de cercle, de la barre d'entraînement (27) est atteinte, pour laquelle une ligne d'action de force de la force de formage à appliquer est alignée avec une ligne d'action de force (49) d'une force de réaction agissant du fait du processus de formage sur la barre de cintrage (30) puis le contrôle des moyens d'entraînement (17, 18) reliés en entraînement avec la barre d'entraînement (27) a lieu pour le réglage de la barre de cintrage (30) vers une position d'emboîtement des outils de cintrage (4) prévue pour le processus de formage prédéterminé sur la pièce à façonner (3).
  15. Procédé selon la revendication 14, caractérisé en ce que, une fois la position d'emboîtement prévue atteinte, les moyens d'entraînement (17, 18) sont contrôlés pour une course de décharge puis le formage sur la pièce à façonner (3), plus particulièrement un angle de formage, est mesuré et si un écart angulaire est constaté, une nouvelle position d'emboîtement est calculée et contrôlée par le réglage de la barre de presse (16), dans lequel, pendant la course de formage de correction, pour la compensation d'éventuelles écarts angulaires par rapport à une longueur de cintrage, un déplacement de la ligne d'action de force a lieu dans la direction de la longueur de cintrage par un pivotement de la barre d'entraînement (27).
EP10000736.8A 2009-01-27 2010-01-26 Presse plieuse dotée d'une poutre d'entraînement et d'une poutre plieuse couplée élastiquement Active EP2210680B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT0013609A AT507808B1 (de) 2009-01-27 2009-01-27 Biegepresse mit einem antriebsbalken und elastisch gekuppelten biegebalken

Publications (3)

Publication Number Publication Date
EP2210680A2 EP2210680A2 (fr) 2010-07-28
EP2210680A3 EP2210680A3 (fr) 2014-12-17
EP2210680B1 true EP2210680B1 (fr) 2021-02-24

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EP10000736.8A Active EP2210680B1 (fr) 2009-01-27 2010-01-26 Presse plieuse dotée d'une poutre d'entraînement et d'une poutre plieuse couplée élastiquement

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2479022A1 (fr) * 2011-01-24 2012-07-25 Osterwalder AG Presse à poudre
DE102011116085A1 (de) * 2011-10-12 2013-04-18 Weinbrenner Maschinenbau Gmbh Biegemaschine
DE102012102594B4 (de) * 2012-03-26 2014-05-08 Siempelkamp Maschinen- Und Anlagenbau Gmbh & Co. Kg Verfahren zum Herstellen von Formteilen aus Kunststoff
CN113526853B (zh) * 2021-08-05 2023-01-06 安徽荣耀光电科技有限公司 一种钢化玻璃加工系统及加工工艺

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Publication number Priority date Publication date Assignee Title
DE4138286A1 (de) * 1991-11-21 1993-05-27 M & S Brugg Ag Presse
JP2819448B2 (ja) * 1994-10-20 1998-10-30 丸機械工業株式会社 油圧プレスブレーキ
ITTO20020904A1 (it) * 2002-10-17 2004-04-18 Alberto Arduino Pressa piegatrce con trave portautensile sostanzialmente

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Publication number Publication date
AT507808B1 (de) 2011-02-15
EP2210680A2 (fr) 2010-07-28
EP2210680A3 (fr) 2014-12-17
AT507808A1 (de) 2010-08-15

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