EP3119538B1 - Auxiliaire de cintrage pour presse plieuse - Google Patents

Auxiliaire de cintrage pour presse plieuse Download PDF

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Publication number
EP3119538B1
EP3119538B1 EP15725983.9A EP15725983A EP3119538B1 EP 3119538 B1 EP3119538 B1 EP 3119538B1 EP 15725983 A EP15725983 A EP 15725983A EP 3119538 B1 EP3119538 B1 EP 3119538B1
Authority
EP
European Patent Office
Prior art keywords
rotary joint
support
support device
distance
pivot
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.)
Active
Application number
EP15725983.9A
Other languages
German (de)
English (en)
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EP3119538A1 (fr
Inventor
Karl BADEGRUBER
Kabir SECIBOVIC
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 EP3119538A1 publication Critical patent/EP3119538A1/fr
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Publication of EP3119538B1 publication Critical patent/EP3119538B1/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
    • B21D5/0281—Workpiece supporting devices
    • 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
    • B21D5/0209—Tools therefor
    • B21D5/0218—Length adjustment of the punch
    • 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
    • B21D43/00—Feeding, positioning or storing devices combined with, or arranged in, or specially adapted for use in connection with, apparatus for working or processing sheet metal, metal tubes or metal profiles; Associations therewith of cutting devices
    • B21D43/02—Advancing work in relation to the stroke of the die or tool
    • B21D43/04—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/14—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work by turning devices, e.g. turn-tables
    • B21D43/145—Turnover devices, i.e. by turning about a substantially horizontal axis
    • 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
    • B21D5/002—Positioning devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D43/00—Feeding, positioning or storing devices combined with, or arranged in, or specially adapted for use in connection with, apparatus for working or processing sheet metal, metal tubes or metal profiles; Associations therewith of cutting devices
    • B21D43/02—Advancing work in relation to the stroke of the die or tool
    • B21D43/04—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/10—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work by grippers
    • B21D43/105—Manipulators, i.e. mechanical arms carrying a gripper element having several degrees of freedom

Definitions

  • the invention relates to a support device for a press brake, as indicated in claim 1.
  • Support devices which are provided to assist in a press brake to be bent sheet metal workpiece during the bending process.
  • the support device can in this case be attached to the front of a press brake.
  • a support pad is formed, on which the sheet metal workpiece to be bent, in particular the rest of the press brake protruding portion of the sheet metal workpiece can rest.
  • the support support is carried along, so that the projecting section of the sheet metal workpiece is supported during the entire bending process.
  • the parallel kinematics is in this case designed so that the pivot axis of the support surface is substantially congruent to the bending axis of the sheet metal workpiece, so that the surface of the support plate can be guided parallel to the surface of the sheet metal workpiece.
  • the movement mechanism of the support device is formed by a parallel kinematic, which can be moved by means of a hydraulic or pneumatic cylinder.
  • the parallel kinematics comprises individual lever arms, which are connected to each other and to a base frame by hinges. At the parallel kinematics further a support pad is arranged with a support surface.
  • the present invention has for its object to provide an improved support device, which is adapted to the dynamic operation of a modern press brake and can handle highly dynamic positioning movements.
  • a support device for a press brake comprising a base frame, at least one base plate arranged for attachment of the support device to a press brake, through which connection plate is formed a perpendicular connection plane, a support surface with a support surface.
  • the support pad can be positioned between a basic position and a maximum position, wherein the support pad is arranged on a lever joint system, which is connected to a positioning drive and designed as a parallel kinematic.
  • the lever joint system has a first main lever arm with a first and a second pivot joint and a second main lever arm with a third and a fourth pivot, which are arranged parallel to one another and are mounted on the base frame by means of the first and the third pivot, which are located in a main bearing plane.
  • a support arm is received by means of the second and fourth pivot, wherein a normal distance between the first and second pivot is the same size as a normal distance between the third and fourth pivot.
  • the second and fourth pivot joints are further spaced from the coupling plane as are the first and third pivot joints.
  • the support support is mounted by means of a fifth pivot, which fifth pivot is arranged on a relative to the fourth pivot protruding part of the support arm.
  • the support support is connected by means of a sixth rotary joint with a support arm, which support arm is connected parallel to the support arm lying by means of a seventh rotary joint with the first or the second Haupthebelarm.
  • the seventh hinge is arranged in extension of the straight line between the first and second pivot joints or between the third and fourth pivot joints.
  • the drive unit comprises a crank connected to the positioning drive, which is designed as a rotary drive, and a rocker articulated thereto, which rocker is connected to the crank by means of an eighth rotary joint and to the lever joint system by means of a ninth rotary joint.
  • a surprising advantage of the design according to the invention is that the known advantages of a lever joint system in the form of a parallel kinematic system can be achieved and, in addition, improved dynamics in the mode of operation of the supporting device and a small installation space can be achieved by the positioning drive. It is advantageous here that the positioning drive can be positioned so that it keeps the installation space of the support device particularly low. By an advantageous articulation of the lever joint system by means of the positioning can be achieved that the forces acting on the hinges radial forces can be reduced because the forces due to the inertia and the acceleration of the individual parts can be minimized. Thus, the entire support device may have a reduced mass, whereby an increased dynamic operation is possible.
  • the rocker is connected by means of the ninth rotary joint with the support arm of the lever joint system.
  • the lever joint system can have an advantageous translation for the conversion of the drive movement in a movement of the support surface.
  • the pendulum support is connected to a portion of the support arm projecting beyond the second rotary joint.
  • crank in particular a connecting line drawn between the center of rotation of the positioning drive and the eighth rotary joint, in the basic position of the supporting support at an acute angle between 1 ° and 20 °, preferably between 2 ° and 10 °, in particular between 4 ° and 8 ° to the rocker, in particular to a drawn between eighth and ninth hinge joint line, are arranged to each other, and that the crank and the rocker in the maximum position of the support pad at an obtuse angle between 160 ° and 179 °, preferably between 170 ° and 178 ° , in particular between 172 ° and 176 ° to each other.
  • the advantage here is that thereby in the two end positions a rotational movement of the positioning with a certain angular velocity to a lower linear velocity at the lever joint system leads, as a rotational movement of the positioning with the same angular velocity in an intermediate position.
  • the exact opposite is the case with the forces to be applied by the positioning drive.
  • the positioning drive in the normal position and in the maximum position of the lever joint system with only a small torque load can apply a high linear force to the lever joint system, since the crank and rocker behave like a toggle lever.
  • the highest forces occur because the dynamic caused by the inertia of the lever joint system forces reach a maximum.
  • it can be achieved that the mass accelerations are reduced because, as already mentioned, the speeds or the speed profile are improved by the positioning drive.
  • the crank of the positioning drive is rotated in the basic position of the support surface so that the crank, in particular a drawn between the center of rotation of the positioning and achtem swivel connecting line, at an angle between 180 ° and 270 °, preferably between 190 ° and 250 °, in particular 220 ° and 240 ° to the connection plane is arranged.
  • the advantage here is that the crank is positioned by this arrangement so that the crank can be advantageously accommodated with the least possible space, and the transmitted forces, and the traversing movements can be designed advantageous.
  • the crank of the positioning drive is rotated in the maximum position of the support surface so that the crank, in particular a drawn between the center of rotation of the positioning and achtem swivel connecting line, at an angle between 0 ° and 45 °, preferably between 5 ° and 20 °, in particular between 7 ° and 15 ° to the connection plane is arranged.
  • the advantage here is that the crank is positioned by this arrangement so that the crank can be advantageously accommodated with the least possible space, and the transmitted forces, and the traversing movements can be designed advantageous.
  • the positioning drive comprises a servomotor.
  • a servo motor is well suited for use in such a machine, since it can apply a high torque, a holding force, or even standstill torque, can apply, and thus does not have to be slowed down.
  • a servo motor can be precisely controlled in its movement and travel position, so that an accurate positioning of the support pad can be made possible.
  • Such a servomotor can further be well controlled by the machine control.
  • the support arm is further distanced from the main bearing plane, as the support arm.
  • the advantage here is that thereby the support arm is arranged in the lever joint system, that it is accommodated as possible to save space.
  • the connecting plate and the base frame an adjusting device is arranged, through which the base frame is adjustable with respect to its position to the connecting plate parallel to the connecting plane in a vertical direction.
  • the advantage here is that thereby the support device is height adjustable.
  • different bending tools can be used with different support heights of the bending die in the press brake, wherein the support device, in particular the support support in its basic position can be adapted to the vertical position of the sheet.
  • the adjusting device comprises a drive motor.
  • the advantage here is that the adjustment of the base frame with respect to the connection plate can be automated by a drive motor.
  • the support device comprises a protective cover, wherein the protective cover consists of a fixed and a mitbewegbaren with the support support portion, and the first Haupthebelarm and / or the support arm at least partially adapted to the inner contour of the protective cover outer contour, in particular circular arc Having outer contour.
  • the protective cover protects the internal components from environmental influences and from contamination. The fact that the individual elements of the lever joint system are adapted to the protective cover, the protective cover can be built as small as possible, whereby space is saved and further the mass to be moved can be kept as low as possible.
  • the distance of the fifth rotary joint to the sixth rotary joint is between 25% and 60%, preferably between 35% and 50%, in particular between 40% and 45% of the distance of the first rotary joint to the second rotary joint and that the fourth Swivel joint to the fifth pivot has an equal distance, as the first pivot to the second pivot.
  • the distance of the ninth rotary joint to the seventh rotary joint is between 5% and 30%, preferably between 10% and 25%, in particular between 15% and 20% of the distance of the first rotary joint to the second rotary joint and that the distance of the eighth rotary joint to the ninth pivot between 110% and 145%, preferably between 120% and 135%, in particular between 125% and 130% of the distance of the first pivot to the second pivot, and that the distance of the center of rotation of the positioning drive to eighth pivot between 45 % and 75%, preferably between 50% and 60%, in particular between 54% and 64% of the distance of the first pivot to the second pivot.
  • lever joint system in combination with the rotary drive, a layout of the lever joint system can be achieved, in which the space is minimized and further the forces occurring in the hinges can be kept as low as possible, since the dynamic forces due to the inertia of the individual Components can be kept as low as possible. As a result, the lever joint system can be adjusted highly dynamically.
  • the distance of the first pivot to the third pivot between 25% and 60%, preferably between 35% and 50%, in particular between 40% and 45% of the distance of the first pivot to the second pivot, and that the horizontal distance of the first pivot to the third pivot between 15% and 40%, preferably between 20% and 35%, in particular between 25% and 30% of the distance of the first pivot to second pivot joint and that the horizontal distance of the center of rotation of the positioning to the third pivot between 35% and 65%, preferably between 40% and 60%, in particular between 45% and 55% of the distance of the first pivot to the second pivot.
  • lever joint system in combination with the rotary drive, a layout of the lever joint system can be achieved, in which the space is minimized and further the forces occurring in the hinges can be kept as low as possible, since the dynamic forces due to the inertia of the individual Components can be kept as low as possible. As a result, the lever joint system can be adjusted highly dynamically.
  • Fig. 1 shows a schematic representation of the side view of a processing plant 1.
  • the processing plant 1 comprises a press brake 2, which is provided for bending a sheet 3.
  • the press brake 2 comprises a first adjustable pressing bar 4, in which a first tool holder 5 for receiving a first bending tool 6 is formed.
  • the first bending tool 6 is hereby preferably designed as a bending punch 6.
  • the press brake 2 comprises a second fixed pressing beam 7 on which a second tool holder 8 for receiving a second bending tool 9 is formed.
  • the second bending tool 9 is preferably designed as a bending die and corresponds to the first bending tool 6.
  • the sheet 3 to be bent is placed on a sheet support surface 10 of the second bending tool 9.
  • the first bending tool 6 or the first adjustable pressing beam 4 is moved by a press drive unit 11 in the vertical direction upwards or downwards.
  • a computer unit 12 is provided, which can be coupled to an input and / or display unit 13.
  • the processing system 1 comprises a manipulation device 14, by means of which the sheets 3 to be processed can be manipulated automatically.
  • the sheets 3 to be processed are placed manually in the press brake 2.
  • a support device 15 can be attached to the press brake 2, which can support a relative to the bending tools 6, 9 far protruding sheet metal leg 16 of the sheet to be machined 3 during the bending process. As a result, it can be prevented that the protruding sheet metal leg 16 bends downwards due to its intrinsic mass and due to the gravitational force and thus deforms unintentionally.
  • the support device 15 comprises a support support 17, on which a support surface 18 is formed.
  • the sheet 3 to be machined can rest on the supporting surface 18 and is guided and supported by the supporting device 15 during the bending process.
  • the support device 15 further comprises a connection plate 19 through which the support device 15 can be attached to the press brake 2.
  • the connecting plate 19 may be connected to the press brake 2.
  • the connecting plate 19 is connected to the press brake 2 by means of a guide rail system, which is designed as a linear guide 20.
  • a linear guide 20 can be provided that the support device 15 in a horizontal direction 21 is adjustable. The adjustment of the support device 15 in a horizontal direction 21 can be done manually or by means of a drive unit as required.
  • a Schnellkuppelü or about a screw can be provided as an alternative means of attachment between the connecting plate 19 and press brake 2, for example, a Schnellkuppelü or about a screw can be provided.
  • all fastening elements known to the person skilled in the art can be used here.
  • connection plane 22 The transition interface between press brake 2 and support device 15 is represented by a connection plane 22.
  • This connection plane 22 is preferably vertically aligned in the operational state of the support device 15 and is thus parallel to an end face 23 of the front side of the press brake 2, on which the support device 15 is mounted.
  • the connection plane 22 thus defines the orientation of the support device 15 in the operating state in which the support device 15 is attached to the press brake 2.
  • All position information such as above, below, etc. refer to the operational state of the support device 15 in which it is attached to the press brake 2.
  • Fig. 2 shows in a side view accordingly Fig. 1 a schematic representation of the support device 15 according to the invention based on which their operation or the structure is explained and described.
  • the support device 15 is illustrated by simplified dashes representing the centerlines of the individual levers.
  • the support device 15 comprises a base frame 24 on which a lever joint system 25 is arranged and on which lever joint system 25 the support support 17 is attached.
  • a lever joint system 25 can be achieved that the support seat 17, in particular the support surface 18, between a basic position 26 and a maximum position 27 can be pivoted.
  • a pivot center 28 of the pivoting movement with the outer bearing edge of the second bending tool 9 is congruent and thus ensured during the entire bending operation or during the entire pivoting process that the sheet to be bent 3, in particular the sheet leg 16 full on the support surface 18 of the support pad 17 rests.
  • an adjusting device 29 is attached, through which the base frame 24th can be adjusted in a vertical direction 30. This is necessary when various bending tools 9 are used, which have different dimensions.
  • the adjusting device 29 can in this case be driven manually, for example by a crank.
  • a drive motor 31 is provided, which is coupled to the computer unit 12 and thus allows automatic height adjustment of the support seat 17.
  • the base frame 24 may be constructed of profiles attached to each other. Furthermore, it is also possible that the base frame 24 is formed from a one-piece cast, steel component or aluminum block.
  • a drive unit 32 is attached, which is provided for the adjustment and positioning of the lever joint system 25.
  • the drive unit 32 is preferably designed as a positioning drive 33 and comprises a rotary drive 34.
  • This rotary drive 34 can be realized approximately by the use of a servomotor.
  • a servomotor may additionally be coupled to a transmission in order to increase the torque or the positioning accuracy.
  • the use of a servomotor has proven to be ideal in that a servo motor can apply a high positioning accuracy and also has a high torque.
  • a servo motor can be very well coupled to the computer unit 12 of the press brake 2 via a corresponding intermediate electronics.
  • the drive unit 32 further comprises a crank 35, which is rotated by the rotary drive 34 about its center of rotation 36.
  • the lever joint system 25 comprises a first main lever arm 37, in which a first and a second pivot 38, 39 are received.
  • lever joint system All components of the lever joint system are described in more detail in an advantageous embodiment of the support device 15 with reference to the following figures or description passages.
  • a lever arm simplified as a center line between two hinges shown and such a center line referred to as a lever arm in the context of this application.
  • the first main lever arm 37 is formed, for example, by a straight line which extends from the center of the first rotary joint 38 to the center of the second rotary joint 39.
  • the length of the first main lever arm 37 is seen as the normal distance between the first and second pivot, in particular between their centers.
  • lever arms are parallel to each other, it is meant that it is a connecting the centers between two hinges straight line of a lever arm, which is parallel to a second connecting the centers between two hinges straight line of another lever arm.
  • a lever arm for example, by design, may be designed as a curved element, wherein for the function of the lever arm exclusively the position of the arranged in the lever arm hinges is relevant to each other.
  • the first main lever arm 37 is fixed to the base frame 24 by means of the first pivot 38.
  • the rotary joints described here can be realized by all known in the art rotary joint types, such as bolts, rolling bearings, etc.
  • the lever joint system 25 further includes a second main lever arm 40 on which a third pivot 41 and a fourth pivot 42 are arranged.
  • the second main lever arm 40 is here attached by means of the third pivot 41 on the base frame 24.
  • the first pivot 38 and the third pivot 41 are in this case in a main bearing plane 43.
  • the main bearing plane 43 also extends through the pivot center 28th
  • the lever joint system 25 further comprises a support arm 44, which is connected by means of the second pivot joint 39 and the fourth pivot 42 with the first Haupthebelarm 37 and with the second Schohebelarm 40.
  • the support arm 44 is in this case designed so that in the installed state of the first Feldhebelarm 37 and the second Schohebelarm 40 are parallel to each other.
  • the support arm 44 is parallel to the main bearing bottom 43.
  • the normal distance 45 between the first pivot 38 and the second pivot 39 is equal to a normal distance 46 between the third pivot 41 and the fourth pivot 42nd
  • the third pivot 41 is here seen in the horizontal direction closer to the connection plane 22 arranged as the first pivot 38. In addition, the third pivot 41 is located higher than that of the first pivot 38.
  • the two main lever arms 37, 40 are in this case oriented so that their second arm 39 and fourth rotary joint 42, which are in communication with the support arm 44, are further away from the connection plane 22 than their first 38 and third pivot joints 41 lying on the main bearing plane 43.
  • the support seat 17 is fixed by means of a fifth pivot 47.
  • the support pad 17 is in this case attached to a part of the support arm 44 protruding from the fourth pivot 42.
  • a support arm 50 is arranged on the support support 17 by means of a sixth pivot 49, which provides for the stabilization of the support support 17.
  • This can be achieved that the space of the support device 15 is kept as low as possible.
  • care must be taken that an extension of these two lines intersects in the pivot center 28.
  • the support arm 50 is connected to the first 37 or the second main lever arm 40 by a seventh hinge 52.
  • the seventh pivot 52 is in this case placed or the lengths of the individual lever arms chosen so that the support arm 50 extends parallel to the support arm 44.
  • the seventh pivot 52 is further arranged in an extension of the straight line 53 between the first and second pivot 38, 39 or between the third or fourth pivot 41, 42.
  • a rocker 54 is provided, which is connected by means of an eighth rotary joint 55 with the already described crank 35 and by means of a ninth rotary joint 56 with the lever joint system 25.
  • connection point of the lever joint system 25 the ninth pivot 56 is arranged. It has proved to be advantageous if the ninth rotary joint 56 is arranged on the support arm 50. However, it is also conceivable that the ninth rotary joint 56 is arranged, for example, on the support arm 44 or on the first or second main lever arm 37, 40.
  • Fig. 3 shows a perspective view of a support device 15 which is in its maximum position 27.
  • a protective cover 57 is formed, by which the internal parts, in particular of the lever joint system 25 is protected from interference.
  • the protective cover 57 is hereby subdivided into a plurality of individual segments, as a result of which it can be moved telescopically with the supporting support 17.
  • a protective bellows 58 is attached, which is intended to cover at a height adjustment of the base frame 24 relative to the connecting plate 19, the inner parts of the support device 15 sufficient.
  • the protective cover 57 comprises an openable side wall 59, through which the rotary drive 34 is accessible for maintenance purposes.
  • Fig. 4 shows the support device 15 in a further perspective view, in which view the protective cover 57 has been hidden to make the lever hinge system 25 visible. It can be clearly seen that the lever joint system 25 is not constructed in a plane, but that this has a certain width, resulting in a three-dimensional structure and thus can be given a certain stability to the whole system.
  • the rotary drive 34 is arranged on a gear 60.
  • This transmission can have two output shafts, wherein a crank 35 can be arranged on each of the two output shafts. These two cranks 35 may be connected to two rockers 54, which may be connected to two support arms 50.
  • all the individual parts of the lever joint system 25 and the drive unit 32 are designed as lightweight as possible, it being possible to provide that within the individual lever recesses are placed through which the lightweight construction is achieved. In order to build the entire system as small as possible, it may also be useful if the individual levers are not designed as simple straight components, but if these are designed as curved parts or have recesses to achieve the best possible nesting of the individual parts to be able to.
  • the second main lever arm 40 or the support arm 44 have at least sections of an outer contour 62 adapted to an inner contour 61 of the protective cover 57.
  • hinges between the lever arms can, as shown in the embodiment, be carried out by means of bolts, which are accommodated in a slide bearing or roller bearing.
  • crank 35 and rocker 54 are in this case preferably designed as a continuous bolt, whereby an undesirable torque generation is avoided. Only the connecting bolts between crank 35 and rocker 54 can not be designed as a continuous bolt for reasons of space.
  • crank 35 or the rocker 54 is at least partially performed as a fork, so that the forces occurring in the eighth swivel joint 55 can be transferred well and there is no unfavorable burden here.
  • the Fig. 5 and 6 show the support device 15 in a side view, wherein the support pad 17 in Fig. 5 is in its maximum position 27 and in Fig. 6 in their basic position 26.
  • Very well visible here are the advantageous dimensions of the lever joint system 25, which are shown in this embodiment.
  • the optimum value ranges of the individual lengths have already been mentioned in the beginning of the benefit description.
  • the value specifications of the geometry of the lever joint system 25 lead to an embodiment in which the internal forces that occur can be minimized and further space can be saved.
  • first angle 63 which is included between crank 35 and rocker 54.
  • the connecting line between the individual pivot joints is the geometrically relevant component.
  • a second angle 64 is relevant, which extends between the crank 35 and the vertical connecting plane 22.
  • the relevant for the nature of the lever joint system 25 geometric dimensions are further the normal distance 65 between the fifth pivot 47 and sixth pivot 49, the normal distance 66 between fourth pivot 42 and fifth pivot 47, the normal distance 67 between ninth pivot 56 and seventh pivot 52, the normal distance 68 between eighth pivot 55 and ninth pivot 56, the normal distance 69 between the center of rotation 36 of the rotary actuator 34 and eighth pivot 55, the normal distance 70 between the first pivot 37 and second pivot 40, and the horizontal distance 71 between the first pivot 37 and third pivot 41 and the Horizontal distance 72 between the first pivot 37 and center of rotation 36 of the rotary drive 34th
  • FIGS. 3 to 6 a further and possibly independent embodiment of the support device 15 is shown, again for like parts, the same reference numerals or component designations as in the preceding FIGS. 1 and 2 be used. In order to avoid unnecessary repetition, the detailed description in the previous ones will be used FIGS. 1 and 2 referred or referred.

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

Claims (16)

  1. Dispositif de soutien (15) pour une presse plieuse (2), comprenant un châssis de base (24), au moins une plaque de liaison (19), disposée sur le châssis de base (24), pour la fixation du dispositif de soutien (15) à la presse plieuse (2), cette plaque de liaison (19) formant un plan de liaison (22) orientée verticalement, un appui de soutien (17) avec une surface d'appui (18), qui peut être positionnée entre une position de base (26) et une position maximale (27), l'appui de soutien (17) étant disposé sur un système d'articulation à levier (25), qui est relié avec une unité d'entraînement (32) et est conçu comme un système cinématique parallèle et le système d'articulation à levier (25) comprenant un premier bras de levier principal (37), avec une première (38) et une deuxième articulation rotative (39), et un deuxième bras de levier principal (40), avec une troisième (41) et une quatrième articulation rotative (42), qui sont disposées parallèlement entre elles et qui sont logées au moyen de la première (38) et de la troisième articulation rotative (41), qui se trouvent dans un plan de palier principal (43), au niveau du châssis de base (24) et sur ces deux bras de levier principaux (37, 40), est logé un bras de support (44) au moyen de la deuxième (39) et de la quatrième articulation rotative (42), une distance normale (45) entre la première (38) et la deuxième articulation rotative (39) étant égale à une distance normale (46) entre la troisième (41) et la quatrième articulation rotative (42) et la deuxième (39) et la troisième articulation rotative (42) étant en outre distantes du plan de liaison (22) comme la première (38) et la troisième articulation rotative (41) et, sur le bras de support (44), l'appui de soutien (17) est logé au moyen d'une cinquième articulation rotative (47), cette cinquième articulation rotative (47) étant disposée au niveau de la partie (48) du bras de support (44) dépassant par rapport à la quatrième articulation rotative (42), l'appui de soutien (17) étant relié au moyen d'une sixième articulation rotative (49) avec un bras de soutien (50), ce bras de soutien (50) étant parallèle au bras de support (44) et relié au moyen d'une septième articulation rotative (52) avec le premier (37) ou le deuxième bras de levier principal (40) et la septième articulation rotative (52) étant disposée dans le prolongement des droites (53) entre la première (38) et la deuxième articulation rotative (39) ou entre la troisième (41) et la quatrième articulation rotative (42), le dispositif d'appui comprenant un entraînement de positionnement (33) conçu comme un entraînement rotatif,
    caractérisé en ce que l'unité d'entraînement (32) comprend un vilebrequin (35) relié avec l'entraînement de positionnement (33) et un bras oscillant (54) relié de manière articulée avec celui-ci, ce bras oscillant (54) étant relié au moyen d'une huitième articulation rotative (55) avec le vilebrequin (35) et au moyen d'une neuvième articulation rotative (56) avec le système d'articulation à levier (25).
  2. Dispositif de soutien selon la revendication 1, caractérisé en ce que le bras oscillant (54) est relié au moyen de la neuvième articulation rotative (56) avec le bras de soutien (50) du système d'articulation à levier (25).
  3. Dispositif de soutien selon la revendication 2, caractérisé en ce que le bras oscillant (54) est relié avec le bras de soutien (50) au niveau d'une portion de celui-ci, dépassant de la deuxième articulation rotative (39).
  4. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que le vilebrequin (35), plus particulièrement une ligne de liaison tirée entre le centre de rotation (36) de l'entraînement de positionnement (33) et la huitième articulation rotative (55), forme, dans la position de base (26) de l'appui de soutien (17), un angle aigu (63) entre 1° et 20°, de préférence entre 2° et 10°, plus particulièrement entre 4° et 8°, par rapport au bras oscillant (54), plus particulièrement par rapport à une ligne de liaison tirée entre la huitième (55) et la neuvième articulation rotative (56), et en ce que le vilebrequin (35) et le bras oscillant (54) forment entre eux, dans la position maximale (27) de l'appui de soutien (17), un premier angle obtus (63) entre 160° et 179°, de préférence entre 170° et 178°, plus particulièrement entre 172° et 176°.
  5. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que le vilebrequin (35) de l'entraînement de positionnement (33) est mis en rotation, dans la position de base (26) de l'appui de soutien (17), de façon à ce que le vilebrequin (35), plus particulièrement une ligne de liaison tirée entre le centre de rotation (36) de l'entraînement de positionnement (33) et la huitième articulation rotative (55), forme un deuxième angle (64) entre 180° et 270°, de préférence entre 190° et 250°, plus particulièrement entre 220° et 240°, par rapport au plan de liaison (22).
  6. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que le vilebrequin (35) de l'entraînement de positionnement (33) est mis en rotation, dans la position maximale (27) de l'appui de soutien (17), de façon à ce que le vilebrequin (35), plus particulièrement une ligne de liaison tirée entre le centre de rotation (36) de l'entraînement de positionnement (33) et la huitième articulation rotative (55), forme un deuxième angle (64) entre 0° et 45°, de préférence entre 5° et 20°, plus particulièrement entre 7° et 15°, par rapport au plan de liaison (22).
  7. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que l'entraînement de positionnement (33) comprend un servomoteur.
  8. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que le bras de soutien (50) est plus éloigné du plan de palier principal (43) que le bras de support (44).
  9. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que, entre la plaque de liaison (19) et le châssis de base (24), se trouve un dispositif de réglage (29), qui permet de régler le châssis de base (24) en ce qui concerne sa position par rapport à la plaque de liaison (19) parallèle au plan de liaison (22) dans une direction verticale (30).
  10. Dispositif de soutien selon la revendication 9, caractérisé en ce que le dispositif de réglage (29) comprend un moteur d'entraînement (31).
  11. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que la plaque de liaison (19) comprend, au niveau de son interface avec la presse plieuse (2), un guidage linéaire (20), de façon à ce que le dispositif de soutien (15) puisse être réglé par rapport à la presse plieuse (2) parallèlement au plan de liaison (22) dans une direction horizontale (21).
  12. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que le dispositif de soutien (15) comprend un couvercle protecteur (57), le couvercle protecteur (57) étant constitué d'une portion pouvant être déplacée avec l'appui de soutien (17) et le premier bras de levier principal (37) et/ou le bras de support (44) présente un contour externe (62) adapté au contour interne (61) du couvercle protecteur (57), plus particulièrement un contour externe en forme d'arc de cercle (62).
  13. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que la distance (65) entre la cinquième articulation rotative (47) et la sixième articulation rotative (49) représente entre 25 % et 60 %, de préférence entre 35 % et 50 %, plus particulièrement entre 40 % et 45 % de la distance (45) entre la première articulation rotative (38) et la deuxième articulation rotative (39) et en ce que la quatrième articulation rotative (42) présente, par rapport à la cinquième articulation rotative (47), une distance (66) égale à la distance entre la première articulation rotative (38) et la deuxième articulation rotative (39).
  14. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que la distance (67) entre la neuvième articulation rotative (56) et la septième articulation rotative (52) représente entre 5 % et 30 %, de préférence entre 10 % et 25 %, plus particulièrement entre 15 % et 20 % de la distance (45) entre la première articulation rotative (38) et la deuxième articulation rotative (39) et en ce que la distance (68) entre la huitième articulation rotative (55) et la neuvième articulation rotative (56) représente entre 110 % et 145 %, de préférence entre 120 % et 135 %, plus particulièrement entre 125 % et 130 % de la distance (45) entre la première articulation rotative (38) et la deuxième articulation rotative (39), et en ce que la distance (69) entre le centre de rotation (36) de l'entraînement de positionnement (33) et la huitième articulation rotative (55) représente entre 45 % et 75 %, de préférence entre 50 % et 60 %, plus particulièrement entre 54 % et 64 % de la distance (45) entre la première articulation rotative (38) et la deuxième articulation rotative (39).
  15. Dispositif de soutien selon l'une des revendications précédentes, caractérisé en ce que la distance (70) entre la première articulation rotative (38) et la troisième articulation rotative (41) représente entre 25 % et 60 %, de préférence entre 35 % et 50 %, plus particulièrement entre 40 % et 45 % de la distance (45) entre la première articulation rotative (38) et la deuxième articulation rotative (39),et en ce que la distance horizontale (71) entre la première articulation rotative (38) et la troisième articulation rotative (41) représente entre 15 % et 40 %, de préférence entre 20 % et 35 %, plus particulièrement entre 25 % et 30 % de la distance (45) entre la première articulation rotative (38) et la deuxième articulation rotative (39) et en ce que la distance horizontale (72) entre le centre de rotation (36) de l'entraînement de positionnement (33) et la troisième articulation rotative (41) représente entre 35 % et 65 %, de préférence entre 40 % et 60 %, plus particulièrement entre 45 % et 55 % de la distance (45) entre la première articulation rotative (38) et la deuxième articulation rotative (39).
  16. Installation de traitement (1) comprenant une presse plieuse (2) avec une première barre de pressage réglable (4), qui comprend un premier logement d'outil (5), et avec une deux barre de pressage réglable (7), qui comprend un deuxième logement d'outil (8), ainsi qu'un dispositif de soutien (15) pour l'appui d'une tôle (3) à traiter, qui peut être fixé au moyen d'au moins une plaque de liaison (19) à la presse plieuse (2), caractérisé en ce que le dispositif de soutien (15) est conçu selon au moins une des revendications précédentes.
EP15725983.9A 2014-03-19 2015-03-16 Auxiliaire de cintrage pour presse plieuse Active EP3119538B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50193/2014A AT515296B1 (de) 2014-03-19 2014-03-19 Biegehilfe für eine Abkantpresse
PCT/AT2015/050066 WO2015139066A1 (fr) 2014-03-19 2015-03-16 Auxiliaire de cintrage pour presse plieuse

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EP3119538A1 EP3119538A1 (fr) 2017-01-25
EP3119538B1 true EP3119538B1 (fr) 2017-11-22

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EP (1) EP3119538B1 (fr)
JP (1) JP6588458B2 (fr)
CN (1) CN106132579B (fr)
AT (1) AT515296B1 (fr)
WO (1) WO2015139066A1 (fr)

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US20170080469A1 (en) 2017-03-23
CN106132579A (zh) 2016-11-16
AT515296A4 (de) 2015-08-15
WO2015139066A1 (fr) 2015-09-24
US10363591B2 (en) 2019-07-30
EP3119538A1 (fr) 2017-01-25
JP2017507787A (ja) 2017-03-23
JP6588458B2 (ja) 2019-10-09
CN106132579B (zh) 2018-11-02
AT515296B1 (de) 2015-08-15

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