• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a supporting device (15) for a press brake, comprising a base frame (24), a support support (17) with a support surface (18) which can be positioned between a basic position (26) and a maximum position (27), wherein the support support (17) on a lever joint system (25) is arranged, which is connected to a drive unit (32) and designed as a parallel kinematic. The drive unit (32) comprises a crank (35) connected to a positioning drive (33), which is designed as a rotary drive (34), and a rocker (54) articulated thereto. The rocker (54) is connected to the crank (35) by means of an eighth swivel joint (55) and to the lever joint system (25) by means of a ninth swivel joint (56).
    公开号:AT515296A4
    申请号:T50193/2014
    申请日:2014-03-19
    公开日:2015-08-15
    发明作者:
    申请人:Trumpf Maschinen Austria Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a support device for a press brake, as indicated in claim 1.
    From EP 0 542 610 B1 and DE 41 26 906 A1 support devices are known, which are provided to support the sheet metal workpiece to be bent during the bending process on a press brake. The support device can in this case be attached to the front of a press brake. On the support device, 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. When the sheet metal workpiece moves upwards during the bending process, 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.
    A disadvantage of the embodiments known from EP 0 542 610 B1 and DE 41 26 906 A1 is that the supporting device is very large, whereby the stand available to the machine operator is very limited. Furthermore, results from the construction shown a high inertia of the individual elements, whereby a required in modern press brakes highly dynamic operation is not or only partially possible.
    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.
    This object of the invention is achieved by the measures according to claim 1.
    According to the invention, a support device for a press brake is formed, 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. At the two main lever arms, 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. On the support arm, 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. The advantage here is that the positioning can be positioned so that it keeps the space of the support particularly low. By an advantageous articulation of the lever gels ksystemes 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.
    Furthermore, it may be appropriate that the rocker is connected by means of the ninth rotary joint with the support arm of the lever joint system. By an articulation of the rocker on the support arm of the lever joint system can be achieved that the lever joint system can have an advantageous translation for the conversion of the drive movement in a movement of the support surface. Thus, a comparatively small drive movement of the positioning can be converted with a small drive path in a relatively large movement of the support surface, which expended by the positioning forces, which occur especially due to the dynamic load, can be kept low.
    In a development, it can be provided that the pendulum support is connected to a portion of the support arm projecting beyond the second rotary joint. The advantage here is that the above-mentioned improved dynamic properties can be achieved particularly well by this training.
    Further, it may be provided that the crank, in particular a between pivot point of the positioning and achtem pivot joint drawn connecting line, in the basic position of the support pad 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 leads in the two end positions a rotational movement of the positioning with a certain angular velocity to a lower linear velocity on the lever joint system, 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. In other words, 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. Especially these two end positions, the highest forces occur because the dynamic caused by the inertia of the lever joint system forces reach a maximum. Furthermore, 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.
    In addition, it may be provided that 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 ordered. 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.
    Furthermore, it can be provided that 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.
    Also advantageous is an expression according to which the positioning drive comprises a servomotor. In particular, a servomotor is well suited for use in such a machine, since it can apply a high torque, a holding force, or even standstill torque, can muster, and thus does not need to be braked. Furthermore, 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.
    Furthermore, it can be provided that 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.
    According to a development, it is possible that between 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. This can be different
    Bending tools are used with different support heights of the bending die in the press brake, the support device, in particular the support support can be adjusted in its basic position to the vertical position of the sheet.
    In a further development it can be provided that the adjusting device comprises a drive motor. The advantage here is that by a drive motor, the adjustment movement of the base frame can be automated with respect to the connection plate.
    Furthermore, it may be expedient that the support device comprises a protective cover, wherein the protective cover consists of a fixed and a mitbewegbaren with the support pad 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 advantage here is that the movable parts of the lever joint system are protected from interference by the protective cover and thereby the risk of injury to a user is reduced. Furthermore, 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.
    In addition, it can be provided that 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. Of surprising advantage here is that 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.
    Furthermore, it may be provided that 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. Of surprising advantage here is that 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.
    In addition, it is possible that the distance of the first pivot to the third pivot is 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 the second pivot and that the horizontal distance of the pivot point of the positioning drive 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. Of surprising advantage here is that 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.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    In each case, in a highly simplified, schematic representation:
    Figure 1 is a side view of a processing plant with a press brake and a support device.
    Fig. 2 is a side view of a schematic representation of a support device;
    3 is a perspective view of an advantageous embodiment of a supporting device;
    4 shows a further perspective view of an advantageous embodiment variant of a support device with hidden protective cover;
    5 shows a side view of an advantageous embodiment variant of a supporting device in a maximum position;
    Fig. 6 is a side view of an advantageous embodiment of a support device in a basic position.
    By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and these position information in a change in position mutatis mutandis to transfer to the new location.
    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. Furthermore, 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. For controlling the press drive unit 11, a computer unit 12 is provided, which can be coupled to an input and / or display unit 13.
    Furthermore, it can be provided that the processing system 1 comprises a manipulation device 14, by means of which the sheets 3 to be processed can be manipulated automatically. Alternatively, it can also be provided that the sheets 3 to be processed are placed manually in the press brake 2.
    In order to process large sheet metal workpieces 3, it is further provided that 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 is possible to prevent the protruding sheet-metal limb 16 from bending downwards due to its intrinsic mass and due to the force of gravity, and thus from being deformed 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.
    There are several different ways in which the connecting plate 19 may be connected to the press brake 2. For example, it may be provided that 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. By such 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.
    As an alternative means of attachment between the connecting plate 19 and press brake 2, for example, a Schnellkuppeleinheit or about a screw can be provided. In principle, all fastening elements known to the person skilled in the art can be used here.
    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 corresponding to FIG. 1 a schematic representation of the supporting device 15 according to the invention on the basis of which its mode of operation or its 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 Flebelge-steering system 25 is arranged and on which Flebelgelenksystem 25, the support pad 17 is attached. By such a Flebel hinge system 25 can be achieved that the support surface 17, in particular its support surface 18, between a basic position 26 and a maximum position 27 can be pivoted. By correct dimensioning of the Flebelgelenksystems 25 ensures that a pivot center 28 of the pivoting movement with the outer bearing edge of the second bending tool 9 is congruent and thus throughout the bending process or during the entire pivoting process is ensured 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.
    In order to ensure that the support surface 18 of the support support 17 is in its normal position 26 on a fleas with the sheet support surface 10 of the second bending tool 9, it can be provided that an adjustment device 29 is mounted between the connecting plate 19 and the base frame 24, through which the base frame 24 can be adjusted in a vertical direction 30. This is necessary when various bending tools 9 are used, which have different dimensions. The adjustment device 29 can be manually driven by a crank in this case. In a further embodiment, it is also possible that a drive motor 31 is provided, which is coupled to the computer unit 12 and thus allows automatic Flöhenverstellung 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.
    On the base frame 24, 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. Such 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. Furthermore, 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. 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. For the sake of simplicity, according to the functional model shown in FIG. 2, a lever arm is shown simplified as a center line between two pivot joints, and such a center line is referred to as a lever arm in the sense of this application.
    For the purposes of this description, 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.
    Is it mentioned that two main 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.
    By means of this simplified functional model used for explanation, however, there are no restrictions on the possibilities for designing a main lever arm or a 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 Haupthebelarm 40. The support arm 44 is in this case designed so that in the installed state of the first Haupthebelarm 37 and the second Haupthebelarm 40 are parallel to each other.
    In addition, the support arm 44 is parallel to the main bearing bottom 43. In other words, the normal distance 45 between the first pivot 38 and second
    Swivel joint 39 is the same size as a normal distance 46 between third swivel joint 41 and fourth swivel joint 42.
    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.
    On the support arm 44, 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. Furthermore, 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.
    It is not absolutely necessary that the bearing surface 18 runs parallel to a connecting line between the fifth pivot joint 47 and the sixth pivot joint 49.
    As shown in Fig. 2, it may be advantageous if the support surface 17, in particular the just described connecting lines between fifth pivot 47 and sixth pivot 49 and an extension of the support surface 18, wedge-shaped to each other and thus form a support bracket 51. This can be achieved that the space of the support device 15 is kept as low as possible. Here, however, 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. For the functionality of the lever joint system 25, it is not essential whether the seventh pivot 52 is arranged on the first main lever arm 37 or on the second main lever arm 40. As a result of the construction described, a straight line which is spanned between the fifth pivot joint 47 and the sixth pivot joint 49 and which runs through the pivot center 28 and lies parallel to the first and the second main lever arms 37, 40.
    Thus results in a pivoting movement of the lever gels ksystemes 25 between basic position 26 and maximum position 27 of the virtual pivot center 28th
    In order to position the lever joint system 25 by means of the drive unit 32, 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.
    It is not essential at which connection point of the Hebelgelenksys-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 wherein it is in its maximum position 27. Here, it is readily apparent that 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 in this case subdivided into a plurality of individual segments, as a result of which the latter can be moved with the supporting support 17 in a telescoping manner.
    Furthermore, it can be provided that at the lower end of the support device 15, a protective bellows 58 is mounted, which is intended to be at a height
    Adjustment of the base frame 24 relative to the connecting plate 19 to cover the inner parts of the support device 15 sufficient.
    Furthermore, it may be expedient if the protective cover 57 comprises an openable side wall 59, through which the rotary drive 34 is accessible for maintenance purposes.
    4 shows the support device 15 in a further perspective view, in which view the protective cover 57 has been hidden in order 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.
    As can be seen, it can be provided that 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.
    According to the embodiment shown here, 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.
    It may be expedient if, for example, 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.
    The individual joints referred to as 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.
    It may be expedient if, with regard to the width of the system, a symmetrical or mirror-symmetrical arrangement of the individual lever elements is selected, so that no tension or internal forces occur as a result of the displacement movement. The individual connecting bolts are in this case preferably designed as a continuous bolt, whereby an undesirable Drehmomentenbil- training is avoided. Only the connecting bolts between crank 35 and rocker 54 can not be designed as a continuous bolt for reasons of space. Here it is expedient if either the 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.
    5 and 6 show the support device 15 in a side view, wherein the support seat 17 is in its maximum position 27 in Fig. 5 and in Fig. 6 in its normal position 26. Very well visible are the advantageous dimensions of the lever hinge 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. Especially in combination with the drive unit 32 according to the invention, 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.
    An important geometric dimension is a first angle 63, which is included between crank 35 and rocker 54. As explained above, the connecting line between the individual pivot joints is the geometrically relevant component. Furthermore, a second angle 64 is relevant, which extends between the crank 35 and the vertical connecting plane 22. The geometrical dimensions relevant for the nature of the lever joint system 25 are furthermore the normal distance 65 between the fifth pivot 47 and the sixth pivot 49, the normal distance 66 between the fourth pivot 42 and the fifth pivot 47, the normal distance 67 between the ninth pivot 56 and the seventh pivot 52. the normal distance 68 between eighth pivot 55 and ninth pivot 56, the normal distance 69 between center of rotation 36 of the rotary drive 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 41st and the horizontal distance 72 between the first pivot 37 and center of rotation 36 of the rotary drive 34th
    Furthermore, in FIGS. 5 and 6, a guide rail 73 is shown, in which the individual segments of the protective cover 57 can be guided.
    FIGS. 3 to 6 show another embodiment of the support device 15, which may be independent of itself, wherein the same reference numerals or component designations are used again for the same parts as in the preceding FIGS. 1 and 2. In order to avoid unnecessary repetition, reference is made to the detailed description in the preceding Figures 1 and 2 or reference.
    The embodiments show possible embodiments of the support device 15, wherein it should be noted at this point that the invention is not limited to the specifically illustrated embodiments thereof, but also various combinations of the individual embodiments are mutually possible and this variation possibility due to the teaching of technical action representational invention in the skill of those skilled in this technical field.
    Furthermore, individual features or combinations of features from the different exemplary embodiments shown and described can also represent independent, inventive or inventive solutions.
    The task underlying the independent inventive solutions can be taken from the description. All statements of value ranges in the present description should be understood to include any and all sub-ranges thereof, e.g. is the statement 1 to 10 to be understood that all sub-areas, starting from the lower limit 1 and the upper limit 10 are included, ie. all sub-areas begin with a lower limit of 1 or greater and end at an upper limit of 10 or less, e.g. 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.
    Above all, the individual embodiments shown in FIGS. 1-2, 3-6 can 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.
    For the sake of order, it should finally be pointed out that for a better understanding of the construction of the support device 15, these or their components have been shown partially unevenly and / or enlarged and / or reduced in size.
    REFERENCE SIGNS LIST 1 processing plant 30 vertical direction 2 press brake 31 drive motor 3 plate 32 drive unit 4 first adjustable pressing bar 33 positioning drive 5 first tool holder 34 rotary drive 6 first bending tool 35 crank 7 second fixed Pressbai- 36 center of rotation ken 37 first Haupthebelarm second tool holder 38 first pivot 9 second bending tool 39 second pivot joint 10 sheet support surface 40 second main lever arm 11 press drive unit 41 third pivot 12 computer unit 42 fourth pivot 13 input display unit 43 main bearing plane 14 manipulation device 44 support arm 15 support 45 normal distance 1-2 16 metal leg 46 normal distance 3-4 17 support support 47 fifth pivot 18 support surface 48th protruding part 19 connecting plate 49 sixth rotary joint 20 linear guide 50 supporting arm 21 horizontal direction 51 supporting angle 22 connecting plane 52 seventh rotary joint 23 end face 53 straight 24 Grundra 54 Rocker arm 25 Lever joint system 55 Eighth swivel joint 26 Starting position 56 Ninth swivel joint 27 Maximum position 57 Protective cover 28 Swivel center 58 Protective bellows 29 Adjustment device 59 Sidewall 60 Transmission 61 Inner contour 62 Outer contour 63 First angle 64 Second angle 65 Normal distance 5-6 66 Normal distance 4-5 67 Normal distance 9 -7 68 Normal distance 8-9 69 Normal distance Center point - 8 70 Normal distance 1-3 71 Horizontal distance 1-3 72 Horizontal distance Center point -1 73 Guide
    权利要求:
    Claims (16)
    [1]
    Supporting device (15) for a press brake (2), comprising a base frame (24), at least one base plate (24) arranged connecting plate (19) for fixing the support device (15) on the press brake (2), through which connection plate (19) a vertically aligned connection plane (22) is formed, a support surface (17) having a support surface (18) which is positionable between a basic position (26) and a maximum position (27), wherein the support support (17) on a lever joint system (25) which is connected to a drive unit (32) and designed as a parallel kinematic, and wherein the lever hinge system (25) has a first main lever arm (37) with a first (38) and a second pivot (39) and second main lever arm ( 40) having a third (41) and a fourth pivot (42), which are arranged parallel to each other and by means of the first (38) and the third pivot (41), which in a main bearing plane (43) lie on the base frame (24) are mounted, and on which two main lever arms (37, 40) has a support arm (44) by means of the second (39) and fourth pivot (42) mounted, wherein a normal distance ( 45) between the first (38) and second pivot (39) is equal to a normal distance (46) between the third (41) and fourth pivot (42) and the second (39) and fourth pivot (42) further from the connection plane ( 22) are distanced as the first (38) and third pivot (41), and on which support arm (44) the support support (17) by means of a fifth pivot (47) is mounted, fifth pivot (47) on one opposite the fourth Pivot (42) projecting part (48) of the support arm (44) is arranged, wherein the support support (17) by means of a sixth pivot (49) with a support arm (50) is connected, which support arm (50) parallel to the support arm (44) lying by means of a seventh rotary joint (52) with the ers the seventh pivot joint (52) is connected in extension of the straight line (53) between the first (38) and second pivot joint (39) or between the third (41) and fourth pivot joint (53). 42), characterized in that the drive unit (32) comprises a crank (35) connected to a positioning drive (33), which is designed as a rotary drive (34), and a rocker (54) articulated thereto; which rocker (54) is connected to the crank (35) by means of an eighth pivot (55) and to the lever joint system (25) by means of a ninth pivot (56).
    [2]
    2. Support device according to claim 1, characterized in that the rocker (54) by means of the ninth rotary joint (56) with the support arm (50) of the lever joint system (25) is connected.
    [3]
    3. Support device according to claim 2, characterized in that the rocker (54) on a second pivot (39) projecting portion of the support arm (50) is connected thereto.
    [4]
    4. Support device according to one of the preceding claims, characterized in that the crank (35), in particular a between the center of rotation (36) of the positioning drive (33) and achtem pivot (55) drawn connecting line, in the normal position (26) of the support support (17 ) at an acute angle (63) between 1 ° and 20 °, preferably between 2 ° and 10 °, in particular between 4 ° and 8 ° to the rocker (54), in particular to between eighth (55) and ninth pivot (56) drawn connecting line, are arranged to each other, and that the crank (35) and the rocker (54) in the maximum position (27) of the support support (17) at an obtuse first angle (63) between 160 ° and 179 °, preferably between 170 ° and 178 °, in particular between 172 ° and 176 ° to each other.
    [5]
    5. Support device according to one of the preceding claims, characterized in that the crank (35) of the positioning drive (33) in the basic position (26) of the support support (17) is rotated so that the crank (35), in particular a medium between rotation at a second angle (64) between 180 ° and 270 °, preferably between 190 ° and 250 °, in particular between 220 ° and 240 ° to the connecting plane (FIG. 22) is arranged.
    [6]
    6. Support device according to one of the preceding claims, characterized in that the crank (35) of the positioning drive (33) in the maximum position (27) of the support support (17) is rotated so that the crank (35), in particular a medium between rotation at a second angle (64) between 0 ° and 45 °, preferably between 5 ° and 20 °, in particular between 7 ° and 15 ° to the connecting plane (FIG. 22) is arranged.
    [7]
    7. Support device according to one of the preceding claims, characterized in that the positioning drive (33) comprises a servo motor.
    [8]
    8. Support device according to one of the preceding claims, characterized in that the support arm (50) is further spaced from the main bearing plane (43), as the support arm (44).
    [9]
    9. Support device according to one of the preceding claims, characterized in that between the connecting plate (19) and base frame (24) an adjusting device (29) is arranged, through which the base frame (24) with respect to its position to the connecting plate (19) parallel to the connecting plane ( 22) in a vertical direction (30) is adjustable.
    [10]
    10. Support device according to claim 9, characterized in that the adjusting device (29) comprises a drive motor (31).
    [11]
    11. Support device according to one of the preceding claims, characterized in that the connecting plate (19) at its interface to the press brake (2) has a linear guide (20), so that the support device (15) with respect to the press brake (2) parallel to the connection plane (22 ) is adjustable in a horizontal direction (21).
    [12]
    12. Support device according to one of the preceding claims, characterized in that the supporting device (15) comprises a protective cover (57), wherein the protective cover (57) consists of a fixed and one with the support support (17) mitbewegbaren portion, and the first Haupthebelarm (37) and / or the support arm (44) at least in sections a to the inner contour (61) of the protective cover (57) adapted outer contour (62), in particular circular arc-shaped outer contour (62).
    [13]
    13. Support device according to one of the preceding claims, characterized in that the distance (65) of the fifth pivot (47) to the sixth pivot (49) between 25% and 60%, preferably between 35% and 50%, in particular between 40% and 45% of the distance (45) of the first pivot (38) to the second pivot (39) and that the fourth pivot (42) to the fifth pivot (47) has an equal distance (66), as the first pivot (38) to the second pivot (39).
    [14]
    14. Support device according to one of the preceding claims, characterized in that the distance (67) of the ninth rotary joint (56) to the seventh rotary joint (52) between 5% and 30%, preferably between 10% and 25%, in particular between 15% and Is 20% of the distance (45) of the first pivot (38) to the second pivot (39) and that the distance (68) of the eighth pivot (55) to the ninth pivot (56) between 110% and 145%, preferably between 120% and 135%, in particular between 125% and 130% of the distance (45) of the first pivot (38) to the second pivot (39), and that the distance (69) of the pivot point (36) from the positioning (33) for eighth pivot (55) between 45% and 75%, preferably between 50% and 60%, in particular between 54% and 64% of the distance (45) of the first pivot (38) to the second pivot (39).
    [15]
    15. Support device according to one of the preceding claims, characterized in that the distance (70) of the first pivot (38) to the third pivot (41) between 25% and 60%, preferably between 35% and 50%, in particular between 40% and 45% of the distance (45) of the first pivot (38) to the second pivot (39), and that the horizontal distance (71) of the first pivot (38) to the third pivot (41) between 15% and 40%, preferably between 20% and 35%, in particular between 25% and 30% of the distance (45) of the first pivot (38) to the second pivot (39) and that the horizontal distance (72) of the center of rotation (36) from the positioning drive (33) to the third Swivel joint (41) between 35% and 65%, preferably between 40% and 60%, in particular between 45% and 55% of the distance (45) of the first rotary joint (38) to the second rotary joint (39).
    [16]
    16. processing system (1) comprising a press brake (2) with a first adjustable pressing beam (4), which has a first tool holder (5) and a second fixed pressing beam (7), which has a second tool holder (8), and a support device (15) for supporting a sheet (3) to be processed, which can be fastened to the press brake (2) by means of at least one connecting plate (19), characterized in that the supporting device (15) is designed according to at least one of the preceding claims.
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    同族专利:
    公开号 | 公开日
    WO2015139066A1|2015-09-24|
    JP2017507787A|2017-03-23|
    EP3119538B1|2017-11-22|
    EP3119538A1|2017-01-25|
    JP6588458B2|2019-10-09|
    AT515296B1|2015-08-15|
    CN106132579A|2016-11-16|
    US20170080469A1|2017-03-23|
    CN106132579B|2018-11-02|
    US10363591B2|2019-07-30|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50193/2014A|AT515296B1|2014-03-19|2014-03-19|Bending aid for a press brake|ATA50193/2014A| AT515296B1|2014-03-19|2014-03-19|Bending aid for a press brake|
    US15/126,627| US10363591B2|2014-03-19|2015-03-16|Bending aid for a press brake|
    EP15725983.9A| EP3119538B1|2014-03-19|2015-03-16|Bending aid for a press brake|
    JP2016557905A| JP6588458B2|2014-03-19|2015-03-16|Device that assists bending with a bending press|
    CN201580014625.6A| CN106132579B|2014-03-19|2015-03-16|Bending auxiliary device for flanging press|
    PCT/AT2015/050066| WO2015139066A1|2014-03-19|2015-03-16|Bending aid for a press brake|
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