EP2006079A1 - Biegemaschine - Google Patents

Biegemaschine Download PDF

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Publication number
EP2006079A1
EP2006079A1 EP08005399A EP08005399A EP2006079A1 EP 2006079 A1 EP2006079 A1 EP 2006079A1 EP 08005399 A EP08005399 A EP 08005399A EP 08005399 A EP08005399 A EP 08005399A EP 2006079 A1 EP2006079 A1 EP 2006079A1
Authority
EP
European Patent Office
Prior art keywords
bending
press
actuator
machine frame
connecting element
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.)
Withdrawn
Application number
EP08005399A
Other languages
German (de)
English (en)
French (fr)
Inventor
Gerhard Sperrer
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 EP2006079A1 publication Critical patent/EP2006079A1/de
Withdrawn legal-status Critical Current

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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/18—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by screw means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
    • B30B1/34—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure involving a plurality of plungers acting on the platen

Definitions

  • the invention relates to a bending machine, in particular a press brake, as described in the preamble of claim 1, and a method for driving a press beam of a bending machine, as described in the preamble of claim 19.
  • the bending of sheets on bending machines is one of the most commonly used forming processes, here mainly the free bending or embossing bending is applied in the V-die.
  • the bending machines used in this case generally comprise a machine frame, a pressing table supporting the machine frame, a pressing tool which supports an upper tool and adjustable along a guide on the machine frame in the direction of the press table, and at least one actuator displacing the pressing beam in the direction of the press table.
  • actuators mainly hydraulic cylinders are used, which are arranged above the press bar and press the press bar down in the direction of the press table or a fixed lower press bar. As a result, a substantially rectilinear bending edge is produced on a sheet metal workpiece positioned between the upper tool and the lower tool.
  • the actuators in the form of pressure cylinders above the press beam and the sometimes enormously high bending forces required between the upper tool and lower tool in the form of compressive forces, they must be compensated in this arrangement by correspondingly high internal tensile forces in the machine frame.
  • the tensile loads and bending loads acting on the machine frame during a pressing process cause slight deformations, even with a very stable construction of the machine frame, which can impair the accuracy of the bending result.
  • the high bending forces cause bending of the C-stands, which must be compensated for by complex measures in order nevertheless to obtain the desired accuracy of the bending operation.
  • the object of the invention is to provide a bending machine, in which the forces required for the bending process are advantageous and the machine frame thereby exposed to the lowest possible loads and thereby also deformations during the bending process or with a simpler construction of the machine frame the same bending accuracy can be achieved.
  • the object of the invention is achieved in that a first adjusting element of the pressing bar in the direction of the press table adjusting actuator is drivingly connected by means of a first connecting element with the adjustable pressing beam and a second actuator of the actuator by means of a second connecting element below a running through a press table support surface horizontal reference plane is drive connected to the machine frame or the press table.
  • a first connecting element with the adjustable pressing beam and a second actuator of the actuator by means of a second connecting element below a running through a press table support surface horizontal reference plane is drive connected to the machine frame or the press table.
  • the stator cross-section which usually has the weakest cross-section approximately at the height of the bending tool, not burdened with a tensile force substantially corresponding to the bending force, but only with a bending moment by an optionally outside the bending plane lying action line of the force resultants of the actuator or the actuators is caused.
  • the action line of the actuators is approximately parallel to the adjustment of the press beam along the guide on the machine frame.
  • the bending or rebounding of a C-frame by the forces to be transmitted in the machine frame generally causes a slight displacement of the upper tool in the vertical direction, to a slight extent in the horizontal direction, whereby even a slight tilting of the upper tool can occur with increasing bending force.
  • This tilting movement especially in a bending operation in which the deflection of the upper beam is to be compensated by a certain crowning of the lower tool, the bending accuracy deteriorate sensitive, since the beginning of the bending deformation of a wide workpiece in the middle of the press beam is still at relatively low bending forces, while the side areas of the workpiece are deformed by the crowning only slightly later at higher bending forces, but even the described tilting effect can occur and the bending accuracy can suffer sensitively.
  • the inventive Relief of the machine frame by the arrangement of the actuators can thus contribute to avoiding this adverse effect.
  • the press beam is driven by only one actuator, it is advantageous if at least two actuators are drive-connected to the press beam.
  • the bending machine is characterized less sensitive to eccentric bending forces, for example, when a bending sequence along the press table several different bending tool combinations are arranged. Furthermore, this is the applied by an actuator in each case tensile force less than if this must be provided only by a single actuator.
  • An advantageous embodiment of the bending press is that adjacent to both ends or end faces of the press table in each case an actuator is arranged substantially in a plane extending through the lower tool and upper tool bending plane.
  • a minimization of the bending moments acting on the machine frame can also be achieved by arranging actuators on opposite sides of the bending plane.
  • symmetrical arrangement of the actuators - provided that the actuators bring the same large tensile forces - resulting from the bending force bending moment on the machine frame is negligible.
  • the actuators are arranged symmetrically with respect to a vertical, perpendicular to the bending plane center plane, since the bending forces are most often introduced in the region of this median plane in the press beam or the press table and thereby inclined positions of the press beam Bending work in the mid-plane is largely prevented.
  • the symmetrical arrangement The actuators with respect to the center plane is advantageously often at the end portions of the press beam, so that the area behind the press beam with the widest possible width remains free for workpieces to be machined.
  • a further development of the bending machine according to the invention consists in that on the machine frame or on the pressing beam, a locking device which fixes the pressing beam in its position relative to the machine frame is formed.
  • This locking device may have the function of a brake, with the movements of the press bar in the shortest possible time or on the shortest possible way can be stopped, as may be required for example from safety regulations out.
  • this locking device can facilitate the assembly or retrofitting of the bending machine, for example, by an actuator can be replaced with raised pressing beam.
  • the locking device can act force-locking, for example, by a clamping effect in the leadership of the press bar or, for example, by the adjustment of the press bar blocking interlocking element, for example in the form of a safety bolt, which passes through the press bars and the machine frame.
  • the locking device can also be formed by a separate, additional actuator that can develop corresponding pressure forces and thereby can transfer the weight of the press beam on the machine frame.
  • a decoupling In connection with a locking device, it may be advantageous for assembly and operation of such a bending machine, if by a decoupling the first connecting element of an actuator with the upper beam or the second connecting element of an actuator with the machine frame or the press table is selectively releasably connected. Thereby, the connection of the actuator with the press beam or the press table or machine frame can be achieved with little effort, for example, when the actuator or one of its control elements for work on the bending machine to be changed in position.
  • the decoupling device may, for example, comprise a movable bolt which produces or releases a positive connection between the adjusting element and the pressing beam or machine frame or press table by the operator manually or by an adjusting device controlled by a control and regulating device of the bending machine.
  • the first connection element of the actuator is fully up to below the lower tool or the second connecting element of the actuator entirely up to above the upper tool adjustable.
  • the actuator can thus be shortened so far that creates a free working space for the manipulation of bending tools on the longitudinal end faces of the press beam and press table.
  • the same advantage is achieved if at least one longitudinal end face of the press table, at least temporarily, a free space for the front-side feeding a lower tool on the press table and an upper tool is formed on the pressing beam.
  • This can optionally be effected by an actuator which can be decoupled from the first connection element or the second connection element and which is adjustable in its position.
  • the decoupling can be done as described above by its own decoupling, wherein the position of the press bar with respect to the machine frame can be fixed by a locking device described above.
  • the adjustment of the actuator can be done for example by a pivoting movement about the non-decoupled connecting element with respect to the bending plane to the rear.
  • the one or more actuators of the bending machine can be advantageously formed by a fluid-operated linear motor, wherein a first actuator comprises a cylinder or a cylinder tube and a second actuator comprises a piston guided in the cylinder and a piston rod leading out of the cylinder, whereby the linear motor as a double-acting Fluid cylinder is formed, which can exert both a compressive force for lifting the press beam and a tensile force for pulling the press bar against the press table during the bending process.
  • the linear motor can be arranged both with upwardly and downwardly pointing piston rod, since the function as a tension member during the pressing process and the arrangement of the connecting elements on the pressing beam or in or below the press table support surface on the press table or on the machine frame and the resulting strain relief of the machine frame can be achieved with both arrangement variants.
  • this is designed as a double-acting hydraulic cylinder, which has already proven itself in the conventional arrangement above the upper press beam.
  • an actuator may also be formed by a spindle drive, wherein an actuating element comprises a drivable spindle and an actuating element comprises a cooperating spindle nut.
  • a spindle drive in the form of a spindle drive is also characterized by a high rigidity and can be operated without a complex hydraulic supply device when the spindle is drivingly connected to an electric motor. In the presence of a hydraulic supply device, the spindle can also be driven by a hydraulically actuated rotary motor.
  • the first connecting element or the second connecting element by means of a positive locking element with the press beam or the machine frame or connected to the press table.
  • the interlocking element can be integrally formed on the connecting element, for example in the form of extensions which engage behind a part of the press beam or machine frame.
  • the interlocking element may be formed by a pin, pin or pin, which may optionally be removed and a simple decoupling of the connecting element of the actuator from the press beam or machine frame or press table allowed, for example with its own decoupling.
  • the pressing beam in both adjustment, so both up and down a possible adjustment of at least 155 mm / s, in particular at least 180 mm / s, preferably of at least 220 mm / s.
  • a rapid traverse function can be achieved, for example, by using a hydraulic cylinder with a high piston area ratio value, ie, the piston bottom surface is substantially larger than the piston rod side piston ring surface and the piston rod retracts much faster than the piston body at a constant flow rate of the hydraulic fluid.
  • actuators This causes a rapid traverse of the press beam down;
  • additional actuators can be provided which can be dimensioned smaller because they only need to overcome the weight forces and inertial forces of the press beam, but do not have to raise the high bending force.
  • the machine frame comprises two substantially vertical C stands. As a result, already existing work processes can be taken over unchanged.
  • the object of the invention is also achieved by a method for driving the press beam, wherein during the pressing process for approaching the press bar to the pressing process for approaching the press bar to the press table, a distance between a drive connected to the press beam first connecting element of a first control element and one with the Machine frame or the press table drive-connected second connecting element of a second actuating element is shortened by a tensile force generated by the actuator and the second connecting element is drivingly connected below a running through a Press Tischauflagefiguration horizontal reference plane with the machine frame or the press table.
  • actuators are arranged on both sides of the bending plane and the sum of the products from the tensile force respectively exerted by the actuators on the press beams with the distance of their respective action line is at least approximately equal to the bending plane on both sides of the bending plane.
  • the force resultant of all actuators on one side of the bending plane thus has a precisely opposite bending moment acting around the bending line as the force result of all actuators on the other side of the bending plane.
  • Fig. 1 shows a bending machine according to the invention in the form of a press brake 1.
  • This essentially comprises a machine frame 2, which is connected in its lower region with a press table 3.
  • This is formed as a solid, upstanding plate with a relatively large thickness, for example, over 100 mm, but can also be designed as a press beam, which does not extend to the bottom.
  • a press table support surface 4 is formed, which carries a lower tool 5 in the form of a die, for example a V-die 6.
  • a pressing beam 7 is arranged, which carries a cooperating with the lower tool 5 upper tool 8 in the form of a male, such as a punch 9.
  • the lower tool 5 and the upper tool 8 together form a bending tool 10, with which a bending edge can be produced in a workpiece, not shown, in a free-bending operation or a stamping bending operation.
  • the pressing beam 7 is formed in the illustrated embodiment, similar to the press table 3 as a massive vertically oriented plate and is mounted by means of a guide 11 in the direction 12 to the underlying press table 3 out adjustable on the machine frame 2.
  • the adjustment of the press bar 7 in the direction 12 along the guide 11 is effected by an actuator 13 which is formed in the illustrated embodiment as a hydraulic cylinder 14.
  • the actuator 13 in this case comprises a first adjusting element 15 here in the form of a piston rod 16 of the hydraulic cylinder 14 and a relative to the first adjusting element 15 adjustable second actuating element 17, here in the form of the cylinder tube 18 of the hydraulic cylinder 14.
  • In the cylinder tube 18 is connected to the piston rod 16 and guided on this acting piston 19, which can be acted upon by pressure ports 20 and 21 on the cylinder tube either on the piston rod side piston ring surface 22 or on the opposite piston bottom surface 23 with pressure medium in the form of hydraulic oil.
  • the pressure ports 20 and 21 are fed by a hydraulic supply system, not shown.
  • the actuator 13 is on the one hand connected to the pressing beam 7, on the other hand with the machine frame 2 or as in the illustrated embodiment with the press table 3.
  • the first control element 15 in the form of the piston rod 16 a first connecting element 24, which is drivingly connected to the pressing beam 7 is, also has the second actuator 17 in the form of the cylinder tube 18, a second connecting element 25 which is drivingly connected to the press table 3.
  • the actuator 13 is thus defined by the first connecting element 24 first power drive point 26 above a defined by the press table support surface 4 reference plane 27 and a defined by the second connecting element 25 second power drive point 28 below the reference plane 27.
  • This bending moment is the smaller, the smaller the distance 32 between the bending plane 30 and the resulting line of action 31 is the tensile forces exerted by the actuators 13, since the bending moment acting in the stator cross-section 29 multiplies substantially by the product of the bending force multiplied by the distance 32 results.
  • the hydraulic cylinder 14 may also be generally referred to as a fluid-operated linear motor 33.
  • Fig. 2 shows a rear view of a by means of Fig. 1 described press brake 1, wherein the same components are provided with the same reference numerals and components, already with reference to Fig. 1 have been described, as a result, will not be explained in more detail.
  • Fig. 2 shows that the machine frame 2 substantially two plate-shaped, vertically standing C-stand 34 and two interconnecting horizontal cross-members 35th includes.
  • the pressing bar 7 can be fixed relative to the machine frame 2 by means of two locking devices 37 in its position.
  • This locking device 37 includes, for example, a securing bolt 38 which is introduced by the locking device 37 in a corresponding bore in the C-stand 34 and thereby can secure the position of the press bar 7 form fit.
  • the locking device 37 may also be formed in the form of a non-positively acting brake with which the pressing bar 7 can be fixed in different positions on the machine frame 2.
  • FIG. 3 Another embodiment of the bending machine according to the invention is in Fig. 3 as a side view and in Fig. 4 shown in a rear view.
  • the actuators 13, 13 ' are arranged so that their lines of action 31, 31' lie in the bending plane 30, whereby the distance 32 between the lines of action 31, 31 'and the bending plane 30 is omitted and by the bending force no bending moment on the Stand cross sections 29, 29, the machine frame 2 is caused because of the actuators 13, 13 'caused force resulting lies in the bending plane 30 and the pressing bar 7 is not required by the bending force supporting moment required or effective.
  • the high bending force is not transmitted as a tensile force in the machine frame 2 and the load of the stator cross sections 29, 29' is substantially lower than in the execution of the actuators as pressure members, the press beams during the pressing process Press down against the press table 3 or a lower press beam.
  • a free space 39 is indicated in dashed lines, which allows a front-side feeding a lower tool 5 on the press table 3 or an upper tool 8 to the pressing bar 7. Since in this embodiment of the press brake 1, the actuator 13 is arranged exactly in the extension of the bending plane 30, additional measures to provide this clearance 39 are provided in this embodiment.
  • the actuator 13, which is drivingly connected with its first connecting element 24 to the pressing beam 7, can be decoupled by means of a decoupling device 40 from the pressing beam 7, including this is previously fixed with the aid of the locking device 37 in its position on the machine frame 2.
  • This decoupling of the first connecting element 24 can, as in 3 and 4 indicated by the extraction of a fastening bolt 41, whereby the first connecting element 24 is decoupled from the pressing bar 17 on the first adjusting element 15 in the form of the piston rod 16 and the piston rod 16 then by completely retracting into the cylinder tube 18, a free space 39 for the frontal mounting or dismounting of bending tools releases.
  • the locking device 37 may alternatively be formed by a support member which removes the weight of the press beam with decoupled actuator 13 on the press table 3.
  • the support member may have a fixed length, so be designed in the form of a strut, but alternatively be formed by a fluid-operated support cylinder.
  • the decoupling in the first connecting element 24 can be logically linked to the previous fixation of the press beam 7 by means of the locking device 37.
  • Fig. 5 shows a further embodiment of the bending machine according to the invention in the form of a press brake 1 in a simplified side view.
  • actuators 13, 13 ' are arranged on opposite sides of the bending plane 30, wherein the distance 32 between the line of action 31 of the actuator 13 and the bending plane 30 is identical to the distance 32' of the action line 31 'to the bending plane 30 the opposite side.
  • the respectively caused by the symmetrically with respect to the bending plane 30 actuators 13, 13 'tensile forces together form a force resultant, which is also in the bending plane 30 and thereby the stator section 29 is again free from a bending force caused by the bending moment load.
  • the actuators 13, 13 ' is further given the dashed space 39 for the assembly and disassembly of upper tool 8 and lower tool 5 at any time.
  • the actuators 13, 13 ' are identical and also have identical distances 32, 32' of their lines of action 31 and 31 'to the bending plane 30, it would also be possible that the actuators 13 and 13' have different dimensions and thus cause different tensile forces can, however, which can be compensated in particular by different distances 32 and 32 'of the respective action lines 31 and 31' to the bending plane 30 and the press bar 17 by the bending force and the tensile forces no bending moment in the machine frame 2 initiates.
  • Fig. 6 shows a side view of another embodiment of a press brake 1 according to the invention, in which the actuator 13 is formed by a spindle drive 43 which comprises a driven by a motor 44, for example an electric motor or a hydraulic motor spindle 45 and a cooperating spindle nut 46.
  • the spindle nut 46 in this case forms the first control element 24 and the spindle 45, the second control element 17. Furthermore, the spindle nut 46 simultaneously forms the first connecting element 24, with which the actuator 13 is drivingly connected to the pressing beam 7 and at the same time a positive locking element 47, with which Actuator 13 is connected to the pressing bar 7.
  • the positive locking element 47 may, as shown in the other figures, in particular by a bolt - as in the fastening bolt 41-, a pin or a pin may be formed.
  • the actuator 13 in the form of the spindle drive 43 or also, for example in the form of a hydraulic cylinder 14, as indicated by dashed lines, pivotally attached to the machine table 3 and the machine frame 2 or even on the pressing beam 7 be.
  • a locking device 37 and a decoupling device 40 is provided on the pressing beam 7, whereby the actuator 13 can be decoupled from the fixed pressing beam 7.
  • Fig. 7 shows a modification of the press brake 1 according to Fig. 1 in which the actuator 13 in the form of a fluid-operated linear motor 33, in particular in the form of a hydraulic cylinder 14 with respect to the embodiment in Fig. 1 installed in reverse orientation.
  • the cylinder tube 18 as the first actuator 15 by means of the first Connecting element 24 is drivingly connected to the pressing beam 7, while the piston rod 16 connected to the piston 19 is drivingly connected as a second adjusting element 17 by means of the second connecting element 25 to the press table 3.
  • the first force application point 26 on the pressing beam again lies above the upper tool 8 and the second force application point 28 below the reference plane defined by the press table support surface 4.
  • the two force application points 26, 28 are above or below the stator cross-section 29 to be relieved of the tensile force or one relieving portion of the machine frame 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Press Drives And Press Lines (AREA)
EP08005399A 2007-06-20 2008-03-22 Biegemaschine Withdrawn EP2006079A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT0095607A AT504640B1 (de) 2007-06-20 2007-06-20 Biegemaschine

Publications (1)

Publication Number Publication Date
EP2006079A1 true EP2006079A1 (de) 2008-12-24

Family

ID=39616296

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08005399A Withdrawn EP2006079A1 (de) 2007-06-20 2008-03-22 Biegemaschine

Country Status (6)

Country Link
US (1) US8393193B2 (cs)
EP (1) EP2006079A1 (cs)
JP (1) JP2010530308A (cs)
AT (1) AT504640B1 (cs)
CZ (1) CZ2009858A3 (cs)
WO (1) WO2008154663A1 (cs)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
WO2016016830A1 (en) * 2014-07-30 2016-02-04 Euromac S.P.A. Press brakes
EP3095534A1 (de) * 2015-05-18 2016-11-23 Trumpf Maschinen Austria GmbH & CO. KG. Biegemaschine

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WO2011070231A1 (en) * 2009-12-11 2011-06-16 Aliko Automation Oy Press brake
FI125471B (fi) * 2009-12-11 2015-10-15 Aliko Oy Ltd Menetelmä särmäyspuristimen rungon muodostamiseksi ja särmäyspuristin
DE102010010743B4 (de) * 2010-03-02 2019-10-24 Wafios Ag Umformmaschine zur Herstellung von Formteilen
EP2650216B1 (en) 2012-04-13 2014-08-13 Airbus Operations GmbH Cooling arrangement
EP2664543B1 (en) 2012-05-16 2016-03-23 Airbus Operations GmbH Method for operating an aircraft cooling system and aircraft cooling system
JP6243752B2 (ja) * 2014-02-25 2017-12-06 株式会社アマダホールディングス プレスブレーキ
EP2933190B1 (en) 2014-04-14 2021-09-15 Airbus Operations GmbH Galley cooling system and method of operating a galley cooling system
AT515521B1 (de) * 2014-07-23 2015-10-15 Trumpf Maschinen Austria Gmbh Biegewinkelmessvorrichtung und Verfahren zum Messen eines Biegewinkels mittels der Biegewinkelmessvorrichtung
US9757783B2 (en) 2015-03-19 2017-09-12 Accurpress America Inc. Method and machine for bending metal
CN106216449A (zh) * 2016-09-19 2016-12-14 湖南晟通天力汽车有限公司 大梁翼板压型模具
DE102016222650B4 (de) 2016-11-17 2022-09-08 Airbus Operations Gmbh Kühlanordnung für eine Bordküche und Verfahren zum Betreiben einer derartigen Kühlanordnung
CN111299362A (zh) * 2019-06-19 2020-06-19 惠州市鑫鹏达机电有限公司 一种折弯机
CN111036745A (zh) * 2019-12-25 2020-04-21 南京海长智能装备有限公司 一种端边折弯的可调节刀具
CN112044992A (zh) * 2020-08-11 2020-12-08 广东职业技术学院 一种可调节的双面折弯机构
CN113680858A (zh) * 2021-08-11 2021-11-23 江苏舒尔驰精密金属成形有限公司 冲压模具折弯回弹快速调节装置
CN116037839A (zh) * 2022-12-28 2023-05-02 西安交通大学 一种轻量化两梁自由式快锻液压机

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JP2010530308A (ja) 2010-09-09
WO2008154663A1 (de) 2008-12-24
CZ2009858A3 (cs) 2010-11-10
AT504640B1 (de) 2008-07-15
US8393193B2 (en) 2013-03-12
AT504640A4 (de) 2008-07-15
US20100251797A1 (en) 2010-10-07

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