EP3095534A1 - Cintreuse - Google Patents

Cintreuse Download PDF

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Publication number
EP3095534A1
EP3095534A1 EP16170125.5A EP16170125A EP3095534A1 EP 3095534 A1 EP3095534 A1 EP 3095534A1 EP 16170125 A EP16170125 A EP 16170125A EP 3095534 A1 EP3095534 A1 EP 3095534A1
Authority
EP
European Patent Office
Prior art keywords
actuator
linear guide
bending machine
receiving portion
machine according
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.)
Granted
Application number
EP16170125.5A
Other languages
German (de)
English (en)
Other versions
EP3095534B1 (fr
Inventor
Egon Danninger
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
Original Assignee
Trumpf Maschinen Austria GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Trumpf Maschinen Austria GmbH and Co KG filed Critical Trumpf Maschinen Austria GmbH and Co KG
Publication of EP3095534A1 publication Critical patent/EP3095534A1/fr
Application granted granted Critical
Publication of EP3095534B1 publication Critical patent/EP3095534B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B21D5/0272—Deflection compensating 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
    • B21D5/02—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
    • B30B15/007—Means for maintaining the press table, the press platen or the press ram against tilting or deflection
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/041—Guides
    • 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 machine, in particular a press brake.
  • the present invention has for its object to provide an improved bending machine.
  • a bending machine in particular a bending press, is formed.
  • the bending machine comprises a machine frame having a first and a second side part, a fixed pressing beam coupled to the machine frame, which extends in a Z-direction oriented in the press brake longitudinal direction between the first and second side part, a cross member which is coupled to the first and the second side part is and extends between them and is arranged at a distance above the fixed press beam, at least one actuator, which is coupled by means of an actuator suspension with the cross member and an adjustable pressing beam, which is coupled by means of the at least one actuator movable with the cross member and in one vertical Y-direction is adjustable relative to the fixed pressing beam.
  • the actuator suspension comprises a first and a second linear guide, wherein the first linear guide for transmitting a force acting in the Y direction vertical force is formed and wherein the second linear guide is adapted to transmit a horizontal force, which in a normal to the Y direction and the Z- Direction standing X-direction acts, the actuator is displaceable by means of the actuator suspension in the Z direction.
  • An advantage of the design according to the invention is that by the actuator suspension, which has a first and a second linear guide, the forces are transmitted well from the adjustable pressing beam on the cross member.
  • the actuator is adjustable in the Z direction and thus the force applied to the adjustable pressing beam in the Z direction can be varied. As a result, for example, occurring during the bending process by the action of deformation of the adjustable press beam can be compensated.
  • the first linear guide comprises an adjusting drive, whereby the at least one actuator is displaceable in the press brake longitudinal direction.
  • the advantage here is that by means of the adjustment of the actuator can be moved in the Z direction. If the adjusting drive is arranged in the region of the first linear guide, this further has the advantage that the adjusting drive is arranged approximately centrally of the actuator, so that it comes through the adjustment of the adjustment or by the adjustment itself, if possible to no jamming of the actuator can.
  • the first linear guide comprises a first connection component, which is designed in the form of a flat sheet, wherein the first connection component has a first receiving portion for connection to the actuator and a second receiving portion for connection to the cross member and wherein the first connection component between the first receiving portion and the second receiving portion has a taper, and thereby the first and the second receiving portion are relative to each other by elastic deformation in the region of the taper about a rotational axis aligned in the X direction relative to each other are relatively rotatable.
  • the advantage here is that the connection component is so flexible or elastic equipped that a slight misalignment of the actuator can be compensated by the connection component.
  • connection component can be given by the taper.
  • the taper is formed by two lateral material cuts in the first connection component, which extend in the Z direction. It can thereby be achieved that the torsional stiffness of the connection component can be reduced or adjusted with respect to a rotational torque about the X-axis.
  • the second linear guide comprises a second connection component, which is designed in the form of a flat sheet, wherein the sheet has a first receiving portion for connection to the actuator and a second receiving portion for connection to the transverse bar and wherein the first and the second receiving portion are relatively rotatable relative to each other about an axis of rotation aligned in the X direction.
  • the advantage here is that the connection component is so flexible or elastic equipped that a slight misalignment of the actuator can be compensated by the connection component. As a result, internal stresses in the bending machine can be largely avoided, whereby the long-term stability and long-term strength of the individual components of the bending machine can be increased.
  • the second attachment component has two cuts in the X direction.
  • the advantage here is that a possibility for elastic deformation of the connection component can be given by the taper.
  • first and / or the second connection component are formed symmetrically about the X direction.
  • the advantage here is that an aligned in the Y direction force, which is introduced into the connection component, does not lead to unbalanced load on the connection components.
  • the connection components are not deformed asymmetrically in a central and normally acting on this force.
  • the adjustable pressing beam of the adjustable pressing beam comprises a third linear guide, in particular a ball linear guide, by means of which the adjustable pressing bar is connected to the actuator.
  • a third linear guide in particular a ball linear guide, by means of which the adjustable pressing bar is connected to the actuator.
  • the ball linear guide the actuator is easily adjustable relative to the adjustable pressing beam in the Z direction.
  • the actuator has a stop surface, which is formed opposite a stop surface of the adjustable press beam, wherein the two stop surfaces are arranged at a distance from each other and that the ball linear guide has a clearance which is greater than the distance of two abutment surfaces to each other.
  • FIG. 1 is a schematic front view of a manufacturing plant 1 for the free bending of sheet metal to be produced workpieces shown. Furthermore, in the FIGS. 1 to 5 Embodiment variants or execution details of the manufacturing plant 1 shown in a schematically simplified representation.
  • the production plant 1 comprises a bending machine 2, in particular a press brake, for the production of the workpieces or workpieces.
  • the bending machine 2 comprises a machine frame 3 also called a base frame.
  • the machine frame 3 of the bending machine 2 may comprise, for example, a base plate 4, on the vertically upstanding, spaced from each other and aligned parallel to each other, a first 5 and a second side part 6 may be arranged. These side parts 5, 6 are preferably connected to each other by a solid, formed for example of a sheet metal part or a welded cross member 7 at their distance from the bottom plate 4 end portions.
  • the side parts 5, 6 may be formed approximately C-shaped to form a free space for the forming of the workpiece.
  • a fixed, in particular on the bottom plate 4 fitting, fixed pressing beam 8 may be attached.
  • This fixed pressing beam 8 can also be referred to as a table bar.
  • a press bar 10, in particular a pressure bar, which is relatively adjustable relative to the fixed pressing beam 8 can be guided guided in linear guides 9.
  • the two pressing beams 8, 10 extend in the press brake longitudinal direction 11.
  • the bending tools can in particular as Bending punch 16 and bending die 17 may be formed.
  • the bending punch 16 can also be referred to as an upper tool and the bending die 17 as a lower tool.
  • the bending machine 2 shown may have as drive arrangement 21 for the adjustable pressing beam 10, namely the pressure bar, at least one, in the illustrated embodiment, two actuators 19.
  • the actuators 19 may be e.g. be fed with electrical energy from a power grid 20 and additionally be connected to a control device 21 line connected.
  • the operation of the bending press 3 can be controlled via a line-connected input terminal 22 connected to the control device 21.
  • the actuators 19 may be e.g. to act electromotive spindle drives, as they are well known.
  • actuator or actuators 19 by hydraulically and / or pneumatically actuable actuating means. Cylinder piston arrangements can be used here. But it would also be other drive means, such as. Eccentric drives, toggle drives, rack drives, etc. conceivable.
  • Fig. 2 is a further and possibly independent embodiment of the bending machine 2 is shown, again for like parts, the same reference numerals or component names as in the preceding Fig. 1 be used. To unnecessary repetitions To avoid, the detailed description in the previous one Fig. 1 referred or referred.
  • Fig. 2 shows a perspective view of the bending machine 2, which is shown partially cut.
  • Fig. 2 the coordinate system used to describe the orientation of the machine.
  • the Z-direction 23 is aligned parallel to the press brake longitudinal direction 11 and thus runs parallel to the longitudinal extent of the pressing bars 8, 10.
  • the Z-direction is oriented horizontally.
  • the Y-direction 24 is vertically aligned.
  • the X-direction 25 is arranged at right angles to the Z-direction 23 and the Y-direction 24 and also extends in the horizontal direction.
  • the actuator 19 is connected by means of an actuator suspension 26 with the cross member 7.
  • the actuator suspension 26 comprises a first linear guide 27 and a second linear guide 28.
  • the first linear guide 27 serves to receive a vertical force 29 acting in the Y direction.
  • the second linear guide 28 serves to receive a horizontal force 30 acting in the X direction.
  • the horizontal force 30 becomes initiated by the vertical force 29 acts on the bending edge 31 of the punch 16 and thus has a horizontal distance 32 relative to the first linear guide 27. This results in the first linear guide 27, a torque which can be intercepted by the second linear guide 28.
  • the first linear guide 27 and the second linear guide 28 may be formed, for example in the form of a profile guide, such as a dovetail guide or other sliding guide.
  • a profile guide such as a dovetail guide or other sliding guide.
  • the linear guides 27, 28 are formed by a ball guide.
  • the first linear guide 27 comprises an adjusting drive 33, by means of which the actuator 19 is displaceable in the press brake longitudinal direction 11.
  • the adjusting drive 33 may for example be integrated directly into the first linear guide 27, be designed as a ball screw.
  • the adjustment 33 is formed approximately by an adjacent hydraulic or pneumatic cylinder or by an adjoining adjusting spindle.
  • a first connection member 34 is formed, which serves for power transmission between the actuator 19 and the first linear guide 27.
  • the first connection component 34 is subsequently in Fig. 3 described in detail.
  • a second connecting member 35 is formed, which serves for transmitting the horizontal force 30 from the actuator 19 to the second linear guide 28 and thus to the cross member 7.
  • the second attachment component 35 is shown in a detail view in FIG Fig. 4 described or illustrated in detail.
  • a third linear guide 36 is formed, through which the actuator 19 can be moved in AbkantpressenlFigsraum 11 relative to the adjustable pressing beam 10.
  • Fig. 2 can be provided particularly well, that the first linear guide 27 is disposed on a bottom 37 of the cross member 7 and that the second linear guide 28 is disposed on a front side 38 of the cross member 7.
  • Fig. 3 shows a perspective view from below of the actuator 19, the first linear guide 27 and the first attachment member 34th
  • the first connection member 34 has a first receiving portion 39 for Audi to the actuator 19 and a second receiving portion 40 for connection to the cross member 7.
  • the first receiving portion 39 may in particular have one or more receiving bores 44 for receiving the actuator 19.
  • the actuator 19 is designed as a double actuator and thus has a first actuator rod 42 and a second actuator rod 43.
  • the first receiving section 39 has two receiving bores 44.
  • the first connection component 34 between the first receiving portion 39 and the second receiving portion 40 has a taper 45, whereby the two receiving portions 39, 40 are relative to each other by elastic deformation about an aligned in the X-direction 25 axis of rotation 41 relative navverwindbar.
  • the axis of rotation 41 is, in particular, a virtual axis of rotation, the possible relative rotation between the first receiving section 39 and the second receiving section 40 being in a very small angular range.
  • the taper 45 is formed by two lateral material cuts 46 which extend in the Z direction 23.
  • the material incisions 46 may have a rounding 47 in their end region facing the rotation axis 41, by which rounding 47 the notch effect is reduced by the lateral material recess 46 and thus a sufficient component rigidity of the first attachment component 34 can be achieved.
  • the first attachment component 34 has a width 48, a length 49 and a thickness 50.
  • a residual length 51 results, in particular, from the length 49 minus the two lateral material incisions 46.
  • the size of the residual length 51 or the thickness 50 of the first attachment component 34 have a significant influence on the torsional rigidity between the first receiving portion 39 and the second receiving portion 40.
  • the first receiving section 39 can twist slightly relative to the second receiving section 40, a slight misalignment of the actuator 19 can be compensated.
  • Fig. 4 shows a perspective view obliquely from above on the bending machine 2, wherein in this view, in particular the second connection member 35 and the actuator 19 are visible.
  • the second connection component 35 has a first receiving portion 52 for connection to the actuator 19 and a second receiving portion 53 for connection to the cross member 7.
  • the first receiving portion 52 is divided by the second receiving portion 53 by two cuts 54 which extend in the X direction 25.
  • the two incisions 54 can be achieved that the first receiving portion 52 relative to the second receiving portion 53 can rotate about a rotation axis 55.
  • the rotation can be the same here as in the first connection component 34 by elastic material deformation.
  • the possibility of relative deformation of the first receiving portion 52 relative to the second receiving portion 53 may be increased by one or more additional cuts 56. Despite the cuts 54, 56 can be achieved that the second attachment member 35 in the X direction 25 has a sufficiently high rigidity in order to transfer the horizontal force 30 and is flexible only in the Y-direction 24.
  • the second linear guide 28 is formed in the form of a flat contact surface 57. In such a trained linear guide 28 only a compressive force can be transmitted.
  • Fig. 5 shows a detailed view of an embodiment of the connection of the actuator 19 to the adjustable pressing beam 10.
  • the components are shown partially in section.
  • the third linear guide 36 is formed in the form of a ball guide and that the actuator 19 has a stop surface 58, which is formed opposite a further stop surface 59 of the adjustable press beam 10.
  • the two stop surfaces 58, 59 are arranged at a distance 60 to each other and that the third linear guide 36 has a clearance which is greater than the distance 60 of the two stop surfaces 58, 59 to each other.
  • FIGS. 1 . 2 . 3 . 4 . 5 shown embodiments form the subject of independent solutions according to the invention.
  • the relevant objects and solutions according to the invention can be found in the detailed descriptions of these figures.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
EP16170125.5A 2015-05-18 2016-05-18 Cintreuse Not-in-force EP3095534B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ATA50406/2015A AT516718B1 (de) 2015-05-18 2015-05-18 Biegemaschine

Publications (2)

Publication Number Publication Date
EP3095534A1 true EP3095534A1 (fr) 2016-11-23
EP3095534B1 EP3095534B1 (fr) 2017-11-29

Family

ID=56014899

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16170125.5A Not-in-force EP3095534B1 (fr) 2015-05-18 2016-05-18 Cintreuse

Country Status (2)

Country Link
EP (1) EP3095534B1 (fr)
AT (1) AT516718B1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111014761A (zh) * 2019-12-13 2020-04-17 西安飞机工业（集团）有限责任公司 一种大跨距弱钢性龙门柔性制孔装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005230881A (ja) 2004-02-20 2005-09-02 Amada Co Ltd 板金加工装置およびその装置を用いた折り曲げ加工方法
JP2005230898A (ja) * 2004-02-23 2005-09-02 Amada Co Ltd 板金加工装置および板金加工装置を用いた折り曲げ加工方法
EP2006079A1 (fr) * 2007-06-20 2008-12-24 Trumpf Maschinen Austria GmbH & CO. KG. Machine de pliage
WO2014085840A1 (fr) * 2012-12-06 2014-06-12 Trumpf Maschinen Austria Gmbh & Co. Kg Presse plieuse

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005230881A (ja) 2004-02-20 2005-09-02 Amada Co Ltd 板金加工装置およびその装置を用いた折り曲げ加工方法
JP2005230898A (ja) * 2004-02-23 2005-09-02 Amada Co Ltd 板金加工装置および板金加工装置を用いた折り曲げ加工方法
EP2006079A1 (fr) * 2007-06-20 2008-12-24 Trumpf Maschinen Austria GmbH & CO. KG. Machine de pliage
WO2014085840A1 (fr) * 2012-12-06 2014-06-12 Trumpf Maschinen Austria Gmbh & Co. Kg Presse plieuse

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111014761A (zh) * 2019-12-13 2020-04-17 西安飞机工业（集团）有限责任公司 一种大跨距弱钢性龙门柔性制孔装置
CN111014761B (zh) * 2019-12-13 2021-02-09 西安飞机工业（集团）有限责任公司 一种大跨距弱钢性龙门柔性制孔装置

Also Published As

Publication number Publication date
EP3095534B1 (fr) 2017-11-29
AT516718A1 (de) 2016-08-15
AT516718B1 (de) 2016-08-15

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