• 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 bending machine (2), comprising a machine frame (3) a fixed pressing beam (8) coupled to the machine frame (3), a cross member (7), at least one actuator (19), which is suspended by means of an actuator suspension (26 ) is coupled to the cross member (7), an adjustable Pressbal- ken (10) which is coupled by means of the at least one actuator (19) movable with the cross member (7) and in a vertical Y direction (24) relative to the fixed Press bar (8) is adjustable. The actuator suspension (26) comprises a first (27) and a second linear guide (28), wherein the first linear guide (27) for transmitting a Y-direction (24) acting vertical force (29) is formed and wherein the second linear guide (28 ) is configured to transmit a horizontal force (30) which acts in an X-direction (25) normal to the Y-direction (24) and the Z-direction (23), the actuator (19) being actuated by means of the Actuator suspension (26) in the Z direction (23) is displaceable.
    公开号:AT516718A1
    申请号:T50406/2015
    申请日:2015-05-18
    公开日:2016-08-15
    发明作者:
    申请人:Trumpf Maschinen Austria Gmbh & Co Kg；
    IPC主号:
    专利说明:

    The invention relates to a bending machine, in particular a press brake.
    From JP2005230881A a bending machine is known in which three actuators act on an adjustable pressing beam, wherein the central actuator is horizontally displaceable in the longitudinal direction of the press beam.
    The present invention has for its object to provide an improved bending machine.
    This object of the invention is solved by the features according to claim 1.
    According to the invention, a bending machine, in particular a bending press, is formed. The bending machine comprises a machine frame having a first and a second side part, a fixed pressing beam coupled to the machine frame, which extends in a Z-direction oriented in the press brake longitudinal direction between the first and second side part, a cross member which is coupled to the first and the second side part is and extends between them and is arranged at a distance above the fixed press beam, at least one actuator, which is coupled by means of an actuator suspension with the cross member and an adjustable pressing beam, which is coupled by means of the at least one actuator movable with the cross member and in one vertical Y-direction is adjustable relative to the fixed pressing beam. The actuator suspension comprises a first and a second linear guide, wherein the first linear guide for transmitting a force acting in the Y direction vertical force is formed and wherein the second linear guide for transmitting a horizontal force is formed, which in a normal to the Y-
    Direction and the Z-direction standing X-direction acts, the actuator is displaceable by means of the actuator suspension in the Z direction.
    An advantage of the design according to the invention is that by the actuator suspension, which has a first and a second linear guide, the forces are transmitted well from the adjustable pressing beam on the cross member. In particular, can be achieved by the inventive design that the actuator in the Z direction is adjustable and thus the force applied to the adjustable pressing beam in the Z direction can be varied. As a result, for example, occurring during the bending process by the action of deformation of the adjustable press beam can be compensated.
    Furthermore, it may be expedient that the first linear guide comprises an adjusting drive, whereby the at least one actuator is displaceable in the press brake longitudinal direction. The advantage here is that by means of the adjustment of the actuator can be moved in the Z direction. If the adjusting drive is arranged in the region of the first linear guide, this further has the advantage that the adjusting drive is arranged approximately centrally of the actuator, so that it comes through the adjustment of the adjustment or by the adjustment itself, if possible to no jamming of the actuator can.
    In addition, it may be appropriate that all installed in the bending machine actuators are displaced in Abkantpressenlängsrichtung. The advantage here is that the force application points can be varied freely by the actuators in the movable pressure bar.
    Furthermore, it can be provided that the first linear guide comprises a first connection component, which is designed in the form of a flat sheet, wherein the first connection component has a first receiving portion for connection to the actuator and a second receiving portion for connection to the cross member and wherein the first connection component between the first receiving portion and the second receiving portion having a taper, and thereby the first and the second receiving portion by means of elastic deformation in the region of the taper about a X-directional axis of rotation to each other are relatively drehverdrehbar. The advantage here is that the connection component is so flexible or elastic equipped that a slight misalignment of the actuator can be compensated by the connection component. As a result, internal stresses in the bending machine can be largely avoided, whereby the long-term stability and long-term strength of the individual components of the bending machine can be increased. In addition, a possibility for elastic deformation of the connection component can be given by the taper.
    Also advantageous is an embodiment according to which it can be provided that the taper is formed by two lateral material cuts in the first connection component, which extend in the Z direction. It can thereby be achieved that the torsional stiffness of the connection component can be reduced or adjusted with respect to a rotational torque about the X-axis.
    According to a development, it is possible that the second linear guide comprises a second connection component, which is designed in the form of a flat sheet, wherein the sheet has a first receiving portion for connection to the actuator and a second receiving portion for connection to the transverse bar and wherein the first and the second receiving portion are relatively rotatable relative to each other about an axis of rotation aligned in the X direction. The advantage here is that the connection component is so flexible or elastic equipped that a slight misalignment of the actuator can be compensated by the connection component. As a result, internal stresses in the bending machine can be largely avoided, whereby the long-term stability and long-term strength of the individual components of the bending machine can be increased.
    Furthermore, it may be expedient that the second attachment component has two cuts in the X direction. The advantage here is that a possibility for elastic deformation of the connection component can be given by the taper.
    In addition, it can be provided that the first and / or the second connection component are formed symmetrically about the X direction. The advantage here is that an aligned in the Y direction force, which is introduced into the connection component, does not lead to unbalanced load on the connection components. Thus, the connection components are not deformed asymmetrically in a central and normally acting on this force.
    Furthermore, it can be provided that the adjustable pressing beam of the adjustable pressing beam comprises a third linear guide, in particular a ball linear guide, by means of which the adjustable pressing bar is connected to the actuator. The advantage here is that the ball linear guide the actuator is easily adjustable relative to the adjustable pressing beam in the Z direction.
    According to a particular embodiment, it is possible that the actuator has a stop surface, which is formed opposite a stop surface of the adjustable press beam, wherein the two stop surfaces are arranged at a distance from each other and that the ball linear guide has a clearance which is greater than the distance of two abutment surfaces to each other. The advantage here is that thereby abut the two abutment surfaces on block with an application of the compressive force between the actuator and adjustable pressing beam to each other. Thus, the high force load, which is exerted by the actuators, not transmitted via the guide balls. Rather, the force load is transmitted by resting the two abutment surfaces together.
    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:
    Fig. 1 is a front view of a production line with a bending press;
    Figure 2 is a perspective view of the bending press with section through the cross member and the adjustable pressing beam.
    3 is a perspective view of the first connection component;
    4 is a perspective view of the second attachment component;
    Fig. 5 is a sectional view of the third linear guide.
    By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals and the same component names, the disclosures contained throughout the 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.
    1 shows a schematic front view of a production plant 1 for the free bending of workpieces to be produced from sheet metal. Furthermore, in the figures 1 to 5 variants or execution details of the manufacturing plant 1 are shown in a schematically simplified representation.
    The production plant 1 comprises a bending machine 2, in particular a press brake, for the production of the workpieces or workpieces. The bending machine 2 comprises a machine frame 3 also called a base frame.
    The machine frame 3 of the bending machine 2 may comprise, for example, a base plate 4, on the vertically upstanding, spaced from each other and aligned parallel to each other, a first 5 and a second side part 6 may be arranged. These side parts 5, 6 are preferably connected to each other by a solid, formed for example of a sheet metal part or a welded cross member 7 at their distance from the bottom plate 4 end portions.
    The side parts 5, 6 may be formed approximately C-shaped to form a free space for the forming of the workpiece. On the side parts 5, 6, a fixed, in particular on the bottom plate 4 fitting, fixed
    Press bar 8 to be attached. This fixed pressing beam 8 can also be referred to as a table bar.
    In the region of the side parts 5, 6 remote from the base plate 8, a press bar 10, in particular a pressure bar, which is relatively adjustable relative to the fixed pressing beam 8 can be guided guided in linear guides 9. The two pressing beams 8, 10 extend in the press brake longitudinal direction 11.
    On opposite, parallel to each other receiving surfaces 12,13 of the two press beams 8,10 tool holders 14,15 can be arranged or configured for assembly with bending tools. The bending tools can be designed in particular as a bending punch 16 and bending die 17. The bending punch 16 can also be referred to as an upper tool and the bending die 17 as a lower tool.
    The bending machine 2 shown may have as drive arrangement 21 for the adjustable pressing beam 10, namely the pressure bar, at least one, in the illustrated embodiment, two actuators 19. The actuators 19 may be e.g. be fed with electrical energy from a power grid 20 and additionally be connected to a control device 21 line connected. By way of example, the operation of the bending press 3 can be controlled via a line-connected input terminal 22 connected to the control device 21.
    The actuators 19 may be e.g. to act electromotive spindle drives, as they are well known.
    Regardless, it would also be possible to form the actuator or actuators 19 by hydraulically and / or pneumatically actuable actuating means. It can find cylinder-piston arrangements application. But it would also be other drive means, such as. Eccentric drives, toggle drives, rack drives, etc. conceivable. All of the above-mentioned execution features or individual features of the description of the figures are mentioned in order to describe an exemplary production plant 1 or bending machine 2. As a result, reference to this description can be made in the invention essential, fol lowing part of the description of the figures. All described individual features are therefore not absolutely necessary for the inventive design and can be omitted or replaced by other features.
    Further details required for the operation of such a bending machine 2, such as safety devices, stop arrangements, control and measuring devices, are omitted from the description to avoid unnecessary length of description.
    FIG. 2 shows a further embodiment of the bending machine 2, which is possibly independent of itself, wherein the same reference numerals or component designations are used again for the same parts as in the preceding FIG. In order to avoid unnecessary repetition, reference is made to the detailed description in the preceding FIG.
    Fig. 2 shows a perspective view of the bending machine 2, which is shown partially cut.
    Also visible in Figure 2 is the coordinate system used to describe the orientation of the machine. The Z-direction 23 is aligned parallel to the press brake longitudinal direction 11 and thus runs parallel to the longitudinal extent of the pressing bars 8, 10. In particular, the Z-direction is oriented horizontally. The Y-direction 24 is vertically aligned. The X-direction 25 is arranged at right angles to the Z-direction 23 and the Y-direction 24 and also extends in the horizontal direction.
    As can be seen from FIG. 2, it is provided that the actuator 19 is connected to the cross member 7 by means of an actuator suspension 26. The actuator suspension 26 includes a first linear guide 27 and a second linear guide 28. The first linear guide 27 serves to receive a force acting in the Y direction vertical force 29. The second linear guide 28 serves to receive a force acting in the X direction horizontal force 30. The horizontal force 30 is initiated by the Verti kalkraft 29 acts on the bending edge 31 of the punch 16 and thus has a horizontal distance 32 relative to the first linear guide 27. This results in the first linear guide 27, a torque which can be intercepted by the second linear guide 28.
    The first linear guide 27 and the second linear guide 28 may be formed, for example in the form of a profile guide, such as a dovetail guide or other sliding guide. Alternatively, it is also possible that the linear guides 27, 28 are formed by a ball guide.
    As is further apparent from FIG. 2, it can be provided that the first linear guide 27 comprises an adjusting drive 33, by means of which the actuator 19 is displaceable in the press brake longitudinal direction 11. The adjusting drive 33 may for example be integrated directly into the first linear guide 27, be designed as a ball screw. Alternatively, it is also conceivable that the adjustment 33 is formed by an adjoining hydraulic or pneumatic cylinder o-by an adjoining adjusting spindle.
    As can also be seen from FIG. 2, provision can be made for a first connection component 34 to be formed in the area of the first linear guide 27, which component serves to transmit power between the actuator 19 and the first linear guide 27. The first connection component 34 will be described in further detail in FIG. 3 in detail.
    Furthermore, it can be provided that in the region of the second linear guide 28, a second connecting member 35 is formed, which serves for transmitting the horizontal force 30 from the actuator 19 to the second linear guide 28 and thus to the cross member 7. The second connection component 35 is described or illustrated in detail in a detail view in FIG. 4.
    Furthermore, it can be provided that between the adjustable pressing beam 10 and the actuator 19, a third linear guide 36 is formed, through which the actuator 19 can be moved in Abkantpressenlängsrichtung 11 relative to the adjustable pressing beam 10.
    As can be seen particularly clearly from FIG. 2, provision may be made for the first linear guide 27 to be arranged on an underside 37 of the cross member 7 and for the second linear guide 28 to be arranged on a front side 38 of the cross member 7.
    3 shows a perspective view from below of the actuator 19, the first linear guide 27 and the first connection component 34.
    As can be seen from FIG. 3, provision can be made for the first connection component 34 to have a first receiving section 39 for connection to the actuator 19 and a second receiving section 40 for connection to the transverse carrier 7. The first receiving portion 39 may in particular have one or more receiving bores 44 for receiving the actuator 19. As can be seen in this embodiment, it can be provided that the actuator 19 is designed as a double actuator and thus has a first actuator rod 42 and a second actuator rod 43. In particular, it may be contiguous that the first receiving section 39 has two receiving bores 44. As can further be seen from FIG. 3, it can be provided that the first attachment component 34 has a taper 45 between the first receiving portion 39 and the second receiving portion 40, as a result of which the two receiving portions 39, 40 are pivoted about an axis of rotation 41 aligned in the X direction 25 relative to each other are relatively verdrehbar. In this case, the axis of rotation 41 is, in particular, a virtual axis of rotation, with the possible relative rotation between the first receiving section 39 and the second receiving section 40 being in a very small angular range.
    In particular, it can be provided that the taper 45 is formed by two lateral material cuts 46 which extend in the Z direction 23. The material incisions 46 may have a rounding 47 in their end region facing the rotation axis 41, by which rounding 47 the notch effect is reduced by the lateral material recess 46 and thus a sufficient component rigidity of the first attachment component 34 can be achieved.
    As can be seen from FIG. 3, the first attachment component 34 has a width 48, a length 49 and a thickness 50. A residual length 51 results, in particular, from the length 49 minus the two lateral material incisions 46. The size of the residual length 51 or the thickness 50 of the first attachment component 34 have a significant influence on the torsional rigidity between the first receiving portion 39 and the second receiving portion 40.
    Due to the fact that in the region of the taper 45, the first receiving section 39 can twist slightly relative to the second receiving section 40, a slight misalignment of the actuator 19 can be compensated.
    4 shows a perspective view obliquely from above on the bending machine 2, wherein in this view in particular the second connection component 35 and the actuator 19 are visible. In particular, it can be seen from FIG. 4 that the second connection component 35 has a first receiving section 52 for connection to the actuator 19 and a second receiving section 53 for connection to the transverse carrier 7.
    The first receiving portion 52 is divided by the second receiving portion 53 by two cuts 54 which extend in the X direction 25. By the two incisions 54 can be achieved that the first receiving portion 52 can rotate relative to the second receiving portion 53 about a rotation axis 55. The rotation can be the same here as in the first connection component 34 by elastic material deformation. By forming the notches 54, in addition to relative rotation, it can also be achieved that the first receiving section 52 can shift slightly in the Y direction 24 relative to the second receiving section 53.
    The possibility of relative deformation of the first receiving portion 52 relative to the second receiving portion 53 may be increased by one or more additional cuts 56. Despite the cuts 54, 56 can be achieved that the second connection member 35 in the X direction 25 has a sufficiently high rigidity to the horizontal force 30 can be transmitted and only in the Y direction 24 is flexible.
    As indicated in FIG. 4, it can be provided that the second linear guide 28 is designed in the form of a planar contact surface 57. In a thus formed linear guide 28 only a compressive force can be transmitted.
    Fig. 5 shows in a detailed view of an embodiment of the connection of the actuator 19 to the adjustable pressing beam 10. Here, the components are shown partially cut. As can be seen from FIG. 5, it can be provided that the third linear guide 36 is designed in the form of a ball guide and that the actuator 19 has a stop face 58, which is formed opposite another stop face 59 of the adjustable pressing beam 10. It can be provided that the two stop surfaces 58, 59 are arranged at a distance 60 to each other and that the third linear guide 36 has a clearance which is greater than the distance 60 of the two stop surfaces 58, 59 to each other. It can thereby be achieved that upon application of a compressive force between actuator 19 and adjustable pressing beam 10, the two stop surfaces 58, 59 are pressed against each other and thus touch each other on block. As a result, a high vertical force 29 between actuator 19 and adjustable pressing beam 10 can be transmitted.
    The embodiments show possible embodiments of the bending machine 2, 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 possible with each other and this possibility of variation due to the teaching of technical flanders by 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, 4, 5 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 structure of the bending machine 2, these or their components have been shown partially unevenly and / or enlarged and / or reduced in size.
    REFERENCE SIGNS LIST 1 manufacturing plant 31 bending edge 2 bending machine 32 horizontal distance 3 machine frame 33 adjustment drive 4 bottom plate 34 first attachment component 5 first side member 35 second attachment member 6 second side member 36 third linear guide 7 cross member 37 bottom cross member 8 fixed press beams 38 front cross member 9 linear guide 39 first receiving portion 10 adjustable pressing bar 40th second receiving portion 11 Abkantpressenlängsrichtung 41 rotation axis 12 first receiving surface 42 first actuator rod 13 second receiving surface 43 second actuator rod 14 first tool holder 44 receiving bore 15 second tool holder 45 taper 16 bending punch 46 lateral material cut 17 Biegegesenk 47 rounding 18 drive assembly 48 width first Anbindungsbau- 19 actuator part 20 power 49th Length first connection construction 21 control device part 22 input terminal 50 thickness first connection construction 23 Z-direction part 24 Y-direction 51 residual length 2 5 X direction 52 first receiving section 26 actuator suspension 53 second receiving section 27 first linear guide 54 incision 28 second linear guide 55 rotation axis 29 vertical force 56 additional incision 30 horizontal force 57 contact surface 58 abutment surface 59 further abutment surface 60 distance
    权利要求:
    Claims (10)
    [1]
    claims
    A bending machine (2), in particular a press brake, comprising: a machine frame (3) having a first (5) and a second side part (6); a fixed pressing beam (8) coupled to the machine frame (3) and extending in a Z-direction (23) aligned in the press brake longitudinal direction (11) between the first (5) and second side parts (6); a cross member (7) coupled to the first (5) and second side members (6) and extending between the side members (5, 6) and disposed above the fixed press beam (8); at least one actuator (19), which is coupled by means of an actuator suspension (26) with the cross member (7); an adjustable pressing beam (10), which is coupled by means of the at least one actuator (19) movable with the cross member (7) and in a vertical Y-direction (24) relative to the fixed pressing beam (8) is adjustable, characterized in that the Actuator suspension (26) comprises a first (27) and a second linear guide (28), wherein the first linear guide (27) for transmitting a Y-direction (24) acting vertical force (29) is formed and wherein the second linear guide (28) for the transmission of a horizontal force (30) which acts in a normal to the Y-direction (24) and the Z-direction (23) stationary X-direction (25), wherein the actuator (19) by means of the actuator suspension ( 26) in the Z direction (23) is displaceable.
    [2]
    2. Bending machine according to claim 1, characterized in that the first linear guide (27) comprises an adjusting drive (33), whereby the at least one actuator (19) in Abkantpressenlängsrichtung (11) is displaceable.
    [3]
    3. Bending machine according to claim 1 or 2, characterized in that all in the bending machine (2) installed actuators (19) in Abkantpressenlängsrichtung (11) are displaceable.
    [4]
    4. Bending machine according to one of the preceding claims, characterized in that the first linear guide (27) comprises a first attachment member (34) which is in the form of a flat sheet, wherein the first attachment member (34) has a first receiving portion (39) for Connection to the actuator (19) and a second receiving portion (40) for connection to the cross member (7) and wherein the first connection member (34) between the first receiving portion (39) and the second receiving portion (40) has a taper (45) and thereby the first (39) and the second receiving portion (40) by means of elastic deformation in the region of the taper (45) about a in the X-direction (25) aligned axis of rotation (41) are relative to each other drehverdreh bar.
    [5]
    5. Bending machine according to claim 4, characterized in that the taper (45) by two lateral material cuts (46) in the first connection member (34) is formed, which extend in the Z direction (23).
    [6]
    6. Bending machine according to one of the preceding claims, characterized in that the second linear guide (28) comprises a second connection member (35) which is in the form of a flat sheet, wherein the sheet has a first receiving portion (52) for connection to the actuator (19) and a second receiving portion (53) for connection to the cross member (7) and wherein the first (52) and the second receiving portion (53) about a in the X direction (25) aligned rotational axis (55) are relatively rotatable relative to each other ,
    [7]
    7. Bending machine according to claim 6, characterized in that the second connection component (35) has two cuts (54) in the X direction (25).
    [8]
    8. Bending machine according to one of claims 3 to 7, characterized in that the first (34) and / or the second connection component (35) are formed symmetrically about the X-direction (25).
    [9]
    9. Bending machine according to one of the preceding claims, characterized in that the adjustable pressing beam (10) comprises a third linear guide (36), in particular a ball linear guide, by means of which the adjustable pressing bar (10) is connected to the actuator (19).
    [10]
    10. Bending machine according to claim 9, characterized in that the actuator (19) has a stop surface (58) which is formed opposite a further stop surface (59) of the adjustable press beam (10), wherein the two stop surfaces (58, 59) in a distance (60) are arranged to each other and that the third linear guide (36) has a clearance which is greater than the distance (60) of the two stop surfaces (58, 59) to each other.
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    同族专利:
    公开号 | 公开日
    EP3095534B1|2017-11-29|
    AT516718B1|2016-08-15|
    EP3095534A1|2016-11-23|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JP2005230898A|2004-02-23|2005-09-02|Amada Co Ltd|Sheet metal working device, and folding method using the same|
    JP4444688B2|2004-02-20|2010-03-31|株式会社アマダ|Sheet metal processing apparatus and bending method using the apparatus|
    AT504640B1|2007-06-20|2008-07-15|Trumpf Maschinen Austria Gmbh|Bending machine i.e. folding press, has control element drive-connected to beam by connecting element, and another control element drive-connected to frame or to table in or below horizontal reference plane running through support surface|
    AT513150B1|2012-12-06|2014-02-15|Trumpf Maschinen Austria Gmbh|press brake|CN111014761B|2019-12-13|2021-02-09|西安飞机工业（集团）有限责任公司|Large-span weak-rigidity gantry flexible hole making device|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50406/2015A|AT516718B1|2015-05-18|2015-05-18|bending machine|ATA50406/2015A| AT516718B1|2015-05-18|2015-05-18|bending machine|
    EP16170125.5A| EP3095534B1|2015-05-18|2016-05-18|Bending machine|
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