• 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 press brake (1) comprising a machine frame (2), a stationary press table (7) connected thereto, a press beam (3) which is adjustably mounted on a guide (10) on the machine frame (2) in a straight line in the direction of the press table (7). 9) and at least one on the pressing beam (9) and on the machine frame (2) attacking drive means (12). The machine frame (2) comprises at least two uprights (3, 4), in particular flat C-stands (5, 6) or O-stands arranged transversely to a bending plane (32) extending from the press table (7) to the pressing beam (9). and a connection support (8) connecting two adjacent uprights (3, 4). In this case, at least one longitudinal section (14) of the connecting carrier (8) or in at least one longitudinal section (25) forms a predominant portion of the carrier cross section (27) forming part section (26) of the connecting carrier (8) by the drive means (12) and this with a carrier base body (28) of the connecting carrier (8) releasably connected.
    公开号:AT513150A4
    申请号:T50566/2012
    申请日:2012-12-06
    公开日:2014-02-15
    发明作者:
    申请人:Trumpf Maschinen Austria Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a press brake according to the preamble of claim 1.
    Such press brakes usually have a vertical working plane, and is located in a conventional embodiment of the adjustable pressing beam above the fixed press table. The press table can be performed like a bar beam as well as the sake of simplicity, however, a fixed press beam is referred to as a press table in this application. In a press brake according to the invention, a bending plane deviating from the vertical direction may also be provided and, in the case of a vertical working plane, the adjustable pressing beam may also be arranged below the fixed press table.
    In such press brakes, it is necessary that before and behind the bending plane sufficient space for the supply or the handling of machined or already machined workpieces is provided. For this reason, generic press brakes usually have in the direction of the bending edge spaced stand, which cause the required distance between the fixed press table and the adjustably mounted pressing beam and where often the adjustable pressing bar is performed.
    As with larger bending edge lengths and / or larger workpiece thicknesses considerable forming forces must be applied to the workpiece, the fixed machine frame must have a high strength and rigidity, including the stand itself are made very stable and they must also be connected to each other stable. Very often there is a construction method in which two so-called C-stands are connected to one another by means of the press table and an upper connection carrier. At the C-stands usually a guide for the upper beam is arranged and supports a drive means for the pressing beam on the fixed machine frame in the region of the stand or on the upper connecting beam. The drive means is formed, for example, as a hydraulic cylinder assembly and the cylinder housing is connected to the fixed connection carrier or the fixed uprights and acts the adjustable piston with a piston rod on the adjustable pressing beam. The cylinder housing of the hydraulic cylinder is supported on the underside of the connection carrier or is attached to the front side. By the former arrangement, results in a very high machine height, without thereby increasing the usable working height, while resulting in the second arrangement, a torsional moment on the connection carrier, which causes adverse deformations of the machine frame or machine frame.
    The object of the invention is to provide a press brake, which simultaneously meets high demands on the bending accuracy with a simple construction of the machine frame and further has a high ease of assembly.
    The object of the invention is achieved by a generic press brake with the characterizing features of claim 1.
    Characterized in that at least one longitudinal portion of the connecting carrier or in at least one longitudinal section a predominant portion of the carrier cross section forming portion of the connecting carrier is formed by the drive means and this is releasably connected to a carrier base body of the connection carrier, the connection carrier can be positioned closer to the bending plane and exist in the arrangement of the drive means fewer restrictions than in a continuous connection carrier. Surprisingly, this embodiment of a connection carrier has no adverse effects on the rigidity of the machine frame. Since the drive means are usually arranged in the vicinity of the stand, a high deformation stiffness N2011 / 26000 -3- of the connection carrier is not of primary importance. The required installation space for the drive means and the connection carrier in this case are not mutually obstructive, but may overlap and the positioning of the connection carrier can be carried out in a stress-relieving manner, whereby a material saving can also be achieved due to smaller, required profile cross-sections. Due to the detachable connection of the drive means with the rest of the connection carrier, a modularity of the machine frame is achieved and can thereby the portability and ease of installation of such a press brake can be increased. The deformations of the machine frame occurring at high forming forces are partially lower or more easily calculated in advance by the embodiment according to the invention, whereby corrections of the forming process are more easily possible.
    An advantageous embodiment of the press brake is that the longitudinal section or partial section formed by the drive means is arranged on an end section of the connection carrier and has a coupling surface which contacts one of the posts. The large driving forces of the drive means are thereby introduced directly into the stator and result in only low loads for the carrier body.
    If the drive means forming a subsection of the connecting carrier is arranged on the side of the connecting carrier facing the pressing beam and the carrier base body has an upper belt bridging the drive means on the side facing away from the pressing beam, the tensile stresses arising upwards during bending of the connecting carrier can be absorbed by the upper belt. Since the drive means on the underside transmits the compressive stresses which occur upward upon deflection of the connecting carrier, only slight stresses of the connecting means used for the detachable connection result. For example, fastening screws in the region of the pressure side, ie on the side facing the pressing beam, can be made smaller. Furthermore, in the case of a continuous carrier main body connecting the two uprights, a demounting of the drive means can be carried out without the rest of the carrier main body having to be specially supported and secured against falling down.
    A flexibly replaceable embodiment of the press brake in which the adverse effects of deformation of the machine frame are reduced at high forming forces is that the uprights are in the form of C-stands, the connecting beam being fixed to the uppermost ends of the bending plane facing the bending plane. Stand is attached and each formed between the attachment point for the connection carrier on the C-stand and a central part of the C-stand, a deformation section with a locally reduced stator stiffness. The occurring at high forming forces bending of the C-stator and associated misalignment of the connecting carrier with the drive means can be reduced, since the connection carrier indeed initiates the forming forces in the C-stator, by the deformation portion with respect to the deformations partially from the main part of the C. Stand is decoupled and the skewing is reduced thereby.
    A structurally simple way to form a deformation section through which the bending of the C-stator as little as possible to the connection carrier to a C-stator is that the arranged between the attachment point of the connection carrier at the upper end of the C-stand and the middle part deformation portion of the has the upper edge of the C-stand outgoing approximately parallel to the bending plane recess, in particular a parallel to the bending plane slot.
    A good decoupling of the deformations of the attachment point of the main part of the C-stand is achieved when in the region of the recess, the cross section of the C-stator relative to adjacent cross-sections is reduced by at least one third.
    If the recess for producing the deformation section is designed in the form of a slot, it can further be provided that the slot can be actively widened by an actuator acting on both sides of the slot. amm N2011 / 26000 -5-
    As a result, the plane of the press beam can be adjusted in a direction parallel to the bending plane.
    The attachment point with the adjoining connection carrier can be aligned approximately parallel to the bending plane under the action of the forming forces, if the attachment point for the connection carrier on the C-stand has a greater distance from the press table than the reduced cross-section of the deformation region on the C-stand.
    If the guide for the pressing beam with the bending plane has aligned guide rails, they need to absorb only small tilting moments, whereby they are exposed to less wear and possibly, can be dimensioned smaller. The guide rails can be mounted on the machine frame, whereby they interact with matching guide elements or guide shoes on the pressing beam, but it is also a reverse arrangement of the guide rails on the pressing beam and the guide elements on the machine frame possible.
    An alternative or additional embodiment may consist in that the guide for the pressing beam on the connection carrier, in particular on the drive means, arranged guide rails comprises. These guide rails may be provided in addition to mounted on the stand guide rails.
    By the storage of the press beam at several points perpendicular bending of the press beam is reduced to the bending plane, which promotes the Umformgenauigkeit.
    A simple and modular construction of the connection carrier results when it comprises two drive means detachably connected to the uprights and a central section detachably arranged between them. The drive means form a supporting part of the connection carrier and is only slightly loaded by the direct connection of the drive means to the stator of the carrier body. N2011 / 26000 -6-
    A structurally simple and yet rigid design of the connection carrier is given if its middle section comprises two spaced apart, parallel to the bending plane plate elements. The height of the plate elements is advantageously at least five times the thickness thereof, whereby a high flexural rigidity of the carrier base body is given with little use of material. Since the connection carrier can be placed by the inventive arrangement of the drive means in the bending plane, the torsional load is low even at high forming forces, which is why a simply constructed carrier body is sufficient.
    The above-described embodiment of the connection carrier with two plate elements allows the pressing bar is at least partially positioned between the plate elements of the connecting carrier in its upper end position and thus can be performed with a greater height and thus bending stiffness without the overall height of the press brake must be increased.
    A simple assembly or assembly of the drive means without separate measures for supporting the carrier base body can take place when parallel to the connection carrier distance from this a two stand connecting auxiliary carrier is arranged and longitudinal sections and / or sections and / or a carrier base body of the connection carrier by means of connecting elements on the auxiliary carrier are fastened.
    To avoid tension between the drive means and the pressing beam, it is advantageous if between these a fixedly connected to a drivable and adjustable drive member of the drive means and the pressing beam, articulated bending element is arranged, which is a pivotability of the press bar relative to the drive means to a for Bending plane perpendicular pivot axis causes. Bending moments resulting from a deflection of the press beam on the drive member, e.g. in the form of a piston rod are thereby reduced, whereby the drive means, e.g. in the form of a hydraulic cylinder, is subjected to lower loads. The Bie -7- gel joint is compared to a pivot bearing backlash and low maintenance and for the small occurring tilt angle advantage.
    In this case, the bending element can be arranged at the end of the drive member and aulweisen perpendicular to the bending plane notches, in which preferably arranged on the pressing beam holding elements, in particular bracket engage. Thus, solely by the direction of the notches in a structurally simple manner, the direction of the relative mobility can be adjusted appropriately. The remaining residual cross section on the bending element is dimensioned such that sufficient operation against break is given during operation of the press brake.
    If the drive means comprises at least two drive elements which are arranged parallel to one another and in particular to the bending plane and act on the pressing beam, a load with lower voltage peaks distributed over several points is produced both on the pressing beam and on the connection carrier. Furthermore, advantageous hydraulic circuits with rapid traverse function (rapid movement of the pressing beam at low force) and pressing function (slow movement of the pressing beam at high force) can be provided, for example, with a plurality of parallel hydraulic cylinders.
    A prediction of the deformations of the connecting carrier occurring during a forming process is facilitated if the latter is formed, at least in sections, symmetrically with respect to a longitudinal center plane of the connecting carrier that is parallel to the bending plane.
    In particular, when the longitudinal center plane of the connection carrier lies in the bending plane, the deformations to be expected are mainly bending deformations, since in this case the torsional moments are small.
    In this context, it is furthermore of great advantage if the adjustment direction of the at least one drive means lies in the longitudinal center plane of the connection carrier, since tilting moments and torsional moments on the connection carrier are also minimized by this measure.
    N2011 / 26000 -8-
    A precise guidance of the press beam, which is largely independent of the deformations of the stator required for Umformkraftübertragung, is made possible when the machine frame comprises at least two load carrier supporting the connection carrier and two of these different, the guide for the pressing beam having guide post.
    When the pressing beam has on its opposite end faces with guide rails on the machine frame cooperating guide shoes which are fastened by means of a hinge element on the pressing beam, no harmful moments are introduced into the guides at a deflection of the press beam and consequent skewed at its ends.
    In such an embodiment, in addition, the hinge elements can be arranged at the level of the neutral fiber of the press beam, whereby no constraining forces are transmitted in the longitudinal direction of the press beam on the lateral stand at a deflection of the press beam.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    Each shows in a highly schematically simplified representation:
    Fig. 1 is a perspective view of a possible embodiment of a press brake according to the invention;
    2 shows the region of the connection carrier of a further embodiment of a press brake;
    3 shows the region of a connection carrier of a further possible embodiment of a press brake;
    4 shows the plan view of a connection carrier of a further possible embodiment of a press brake;
    5 shows a section through a press brake according to FIG. 1; N2011 / 26 -9-
    Fig. 6 is a side view of an embodiment of a press brake;
    Figure 7 is a partial view of a press brake with possible embodiments of guides and a possible connection of a drive means on the pressing beam.
    8 shows an alternative embodiment of a connection of the drive means to the pressing beam;
    Fig. 9 is a perspective view of another possible embodiment of a press brake;
    10 shows a section through a possible embodiment of the connection carrier 8.
    11 shows a section through a further possible embodiment of the connection carrier 8;
    Fig. 12 is a view of a possible embodiment of the guide of the press bar on the machine frame.
    1 shows a perspective view of a possible embodiment of a press brake 1 according to the invention. This comprises a machine frame 2, which can also be referred to as a machine frame, and the further components of the press brake are formed, fastened or adjustably mounted thereon. The machine frame 2 comprises two mutually distanced stand 3, 4, which are designed in the illustrated embodiment as a so-called C-stand 5, 6. These are essentially provided with a respective operator-side recess vertically standing plates in C-shape, which are connected at their lower ends with a fixed press table 7 and are connected at their upper ends by means of a connecting carrier 8. The press table 7 cooperates in the operation of the press brake 1 with an adjustably mounted pressing bar 9 and is defined by press table 7 and 9 pressing beam a bending plane. At the press table 7 and at the press beam 9 tool holders are formed.
    Detection tools, not shown, can be attached to perform the desired forming operations on workpieces.
    The adjustable pressing beam 9 is mounted on the machine frame 2 by means of a guide 10, wherein the guide 10, for example guide rails 11, may comprise on the uprights 3, 4 which cooperate with guide elements on the pressing beam 9. In addition, a guide 10 may also be provided on the fixed connection carrier 8.
    The adjustment of the press beam 9 relative to the machine frame 2 by means of at least one drive means 12, which comprises two hydraulic cylinders 13 in the illustrated embodiment. Alternatively or additionally, electrically driven embodiments are possible in addition to hydraulically acting drive means, e.g. with electric motor drive. The drive means 12 acts on the stationary machine frame 2 and on the adjustable pressing beam 9 and generates the forces required during operation of the press brake 1 for the movement of the press beam 9. On the closer version and the operation of the drive means 12, since largely known from the prior art omitted at this point.
    The drive means 12 forms a detachable module of the connection carrier 8 and thus also of the machine frame 2 and forms an essential supporting component in the construction of the machine frame 2. The mechanically supporting component of the drive means 12 may be formed for example in a hydraulic cylinder through the cylinder housing or by another housing the drive means 12.
    According to the invention, the drive means 12 forms a longitudinal section 14 of the connection carrier 8 connecting the uprights 3, 4 and is detachably connected to the remaining base body of the connection carrier 8, which in FIG. 1 is a middle section 15 of the connection carrier 8. In Fig. 1, the two hydraulic cylinders 13 form the two ends of the connecting support 8 and are further releasably connected to the uprights 3, 4. The drive means 12 have to coupling surfaces that contact the stand 3.4. The detachable connection can
    N2011 / 26000 -11 - can be produced by a wide variety of fasteners, such as screw, pin, wedge, etc.
    In contrast to known from the prior art embodiments of press brakes, in the embodiment according to the invention, the drive means 12 is not supported on the connection carrier 8 or on one of the stands 3, 4, but is a force-transmitting component of the connection carrier 8. Das Antriebsmitte! 12 thus not only introduces forces into the connection carrier 8, but is an integral part of the machine frame 2 and contributes directly to its deformation behavior.
    In the embodiment of a press brake illustrated in FIG. 1, its structure could also be described such that the main body of the connecting support 8, which is formed essentially from the middle section 15, is connected to the uprights 3, 4 by means of the drive means 12.
    In Fig. 1, a further possible embodiment of the press brake 1 according to the invention is included, wherein the connecting carrier 8 is fixed to the bending plane, upper ends of the C-stands 5, 6 and wherein between the attachment points 16 of the connection carrier 8 on the C-stand 5, 6 and a respective central part 17 of the C-stand 5.6, a deformation section 18 is formed with a locally reduced stator stiffness. The connecting carrier 8 connecting the two C-stands 5, 6 to the attachment points 16 thus has a slight mobility with respect to the rest of the C-stands 5, 6. As a result, the connecting carrier 8 can be moved even with a slight bending of the C-stands 5, 6 remain a vertical direction, whereby an undesirable relative displacement of the bending tools to each other can be largely prevented.
    In the exemplary embodiment according to FIG. 1, the deformation section 18 is formed by starting from the upper edge of a C-stand 5, 6 a recess 19 extending approximately parallel to the bending plane, in particular in the form of a slot 20, and thereby the previously described slight deformability of the attachment point 16 is effected. As further illustrated in FIG. 1, the middle section 15 of the connecting support 8 may comprise two plate elements 21 parallel to the bending plane. Due to this distance between the two plate elements 21, it is further possible for the pressing beam 9 to have a higher cross section in its middle region and to be positioned at least partially between the plate elements 21 of the connecting carrier 8 when the pressing beam 9 is raised. As a result, the rigidity of the press beam 9 can be further increased without the overall height of the press brake 1 increasing.
    FIGS. 2 and 3 show two possible alternative embodiments of connecting beams 8.
    1, the drive means 12 each have a longitudinal portion 14 of the connecting carrier 8. The drive means 12 are arranged in the illustrated embodiment at the ends of the connecting carrier 8 and contact with coupling surfaces 22 the two mutually distanced stand 3, 4, for example in the form of C-stands 5, 6. The connecting support 8 further comprises the middle section 15 extending between the drive elements 12.
    As FIG. 2 further indicates by dashed lines, drive means 12 can also be provided in the interior, for example in the central region of the connecting carrier 8, thereby forming further longitudinal sections 14 of the connecting carrier 8.
    The drive means 12 are detachably connected to the rest of the connection carrier 8, in this case the middle section 15, wherein this connection is effected by means of connection means 23 symbolically indicated. The connecting carrier 6 is also releasably connected to connecting means 23 with the uprights 3, 4. As connecting means 23 while screws, bolts, pins, wedges, etc. can be used, which allow a stable and backlash-free connection of the drive means 12 with the other parts of the connecting member 8 and the uprights 3, 4. In Fig. 2, the bending plane is parallel to the plane of the drawing.
    Since the pressing beam 9 is bent upwards during the forming of a workpiece, in particular under high forming forces, an additional arrangement of a drive means 12 in the middle region of the connecting carrier 12, which acts on the central region of the pressing beam 9, is suitable for deflecting the deflections Press beam 9 and related geometry errors on the formed workpiece to reduce or prevent.
    In FIG. 2, an adjustment direction 24 of the pressing means 9, which is moved by the drive means 12 by means of driven, movable drive elements, is shown by double arrows.
    3 shows an alternative embodiment of a connecting carrier 8, in which a drive means 12 forms a partial section 26 of the connecting carrier 8 in a longitudinal section 25 of the connecting carrier 8 and this partial section 26 forms the predominant portion of the carrier cross section 27 and this partial section 26 forms with the remainder of the connecting carrier 8 is releasably connected. Examples of such composed of the drive means 12 and a remainder of the connecting carrier 8 carrier cross-sections 27 are shown in further Figs. 10 and 11.
    The formed by the drive means 12 portion 26 of the connecting member 8 is bound by the releasable connection in the power flow between the uprights 3, 4 and thereby a supporting part of the connection support 8. The rest of the connecting support 8, which is not formed by a drive means 12 may Also referred to as a carrier body 28, as well as the center portion 15 shown in Figs. 1, 2 and 3 in Fig. 1 forms a carrier body 28. The longitudinal section 14 in FIGS. 1 and 2 or the partial section 26 in FIG. 3 thus replaces a part of the carrier main body 28 and supplement this to form a complete, modularly constructed connection carrier 8.
    In Fig. 3, the drive means 12, which form portions 26 of the connection carrier 8, arranged at the two end portions of the connecting carrier 8 and contact as well as in Fig. 2 with coupling surfaces 22, the stator 3, 4 and the C-stand 5.6 , In this case, a releasable connection by means of connecting means 23 is also provided between the drive means 12 and the uprights 3,4. N2011 / 26000
    3, the partial section 26 formed by the drive means 12 is bridged in the longitudinal section 25 of the support base body 28, wherein this is executed in the illustrated embodiment as a top flange 29 with a rectangular cross-section. The support base 28 may be embodied, for example, as I-beam and in the longitudinal sections 25 for insertion of the drive means 12 have corresponding Ausklin-kungen. In order to be able to produce a stable, detachable connection of the carrier main body 28 with the drive means 12, end plates 30 can be used on the carrier main body 28 in the region of the notch.
    In the embodiment according to FIG. 3, the drive means 12 forming a partial section 26 of the connecting carrier 8 is arranged on the side of the connecting carrier 8 facing the pressing bar 9 and the upper belt 29 bridging the drive means 12 is arranged on the side of the connecting carrier 8 facing away from the pressing bar 9.
    The top flange 29 is advantageously connected to the uprights 3,4 tensile strength and is further arranged at a deflection of the connecting beam 8 up on the tension side. The drive means 12 is arranged at a deflection of the connecting carrier 8 upwards on the pressure side and is thus effectively clamped between the carrier base body 28 and the uprights 3, 4 and thereby results in lower stresses on the pressure side for the connecting elements 23. The connecting elements 23 are on the connection points between the carrier body 28 and Antriebsmittei 12 or between the drive means 12 and stands 3.4 advantageously arranged at least in pairs and in the direction of deflection of the connecting member 8, which also bending moments can be transmitted to this detachable connection and the components of the machine frame 2 thereby stiffen each other.
    Fig. 4 shows a view according to arrow IV in Fig. 1, in which the region of the attachment point 16 of the connection carrier 8 is shown with the stator 3 of the press brake 1 in a further possible embodiment, which emphasizes the modularity of the press brake 1 according to the invention. IM2011 / 26000 -15- 07-.12 ^ 2012
    The connecting beam 8 has at its end portion successively formed by two drive means 12 longitudinal sections 14, wherein the left in Fig. 4 drive means 12 and the right in Fig. 4 drive means 12 are connected by using connecting means 23 releasably connected to the carrier body 28 and the Both drive means 12 are also releasably connected to each other by means of connecting elements 23. The drive means 12, for example in the form of hydraulic cylinders, are preferably in their longitudinal center plane 31 of the connection carrier 8 and is advantageously also the support base 28 or the entire connection support 28 at least partially symmetrical with respect to the longitudinal center plane 31, which further preferably with the between press table 7 and pressing bar 9 clamped bending plane 32 coincides.
    Due to the fact that the adjustment direction 24 or the plane of action of the drive means 12 coincides both with the longitudinal center plane 31 of the connection carrier 8 and with the bending plane 32, no or only very small torsional moments are introduced into the connection carrier 8 by the forming forces. As already shown in FIG. 1, the carrier base body 28 may comprise two mutually parallel, distanced plate elements 21. The intermediate space between such two plate elements 21 can simultaneously form a movement space for the pressing beam 9.
    Fig. 4 shows, as in the preceding Figs. 1 to 3, a press brake 1 with a plate-shaped stator 3 in the form of a C-stand 5, but the invention also relates to all possible other stator forms, such as O-stand , Pillar stand, hollow profile stand, etc.
    Fig. 5 shows a sectional view of a press brake 1 according to embodiment Fig. 1, wherein the cutting plane is vertical and perpendicular to the bending plane 32.
    The sectional view shows that the pressing beam 9 is positioned with its central region in the raised position in the space between the plate elements 21 of the connecting carrier 8 and the pressing bar 9 through this
    N2011 / 26000 aasseäs
    -16-
    Interspace can be performed in its central region with a much greater height than in its end, in which the drive means 12 attack. Since the bending moments have their maximum mostly in the middle region on the pressing beam 9, this enlarged cross section of the pressing beam 9 is advantageous for its rigidity.
    As can be seen easily from FIGS. 1 and 5, the connection carrier 8 is held in its position via the detachable connection between the drive means 12 and the stand 3. Now, if the replacement of a drive means 12 is required on the connection support 8, this is to be secured in a suitable manner against an unwanted drop, for example, in which a weight is carried by a provisional support. It is advantageous, however, if an auxiliary carrier 33 is provided parallel to the connection carrier 8, to which during the replacement of individual components of the connection carrier 8, the remaining, remaining components are connected by means of suitable connecting means with the auxiliary carrier 33 and carried by this. Thus, for example, the carrier base body 28, in FIG. 5 in the form of two plate elements 21, can be fixed in position with respect to the auxiliary carrier 33 by means of a connecting means 34, for example a bolt 35, and the drive means 12 can subsequently be dismounted.
    Fig. 6 shows a side view of the press brake 1 according to FIG. 1 from the left direction. One recognizes the simply constructed machine frame 2, which consists essentially of the two mutually spaced stands 3, 4 in the form of the C-stand 5, 6, which are connected to each other in the region of the bending plane 32 via the press table 7 and the connection carrier 8. Fig. 6 also shows the optional recess 19 in the form of a slot 20, whereby the C-stator 5 in the region of the slot 20 has a cross-section 36 which is substantially smaller than the adjacent cross-sections 37 of the C-stand 5, whereby a Deforming portion 18 is formed, which causes a locally reduced stator stiffness for the attachment point 16 of the connection carrier 8 on the C-stator 5 and 5 only small torsional moments are transmitted between the connection carrier 8 and C-stator. In case of a possible bending of the C-stand N2011 / 26000 5, the connecting support 8 does not necessarily have to tilt back to the same extent and the connecting support 8 and the press beam 9 connected to it can remain substantially parallel to the bending plane 32.
    FIG. 7 shows a partial view of the connection of the press beam 9 to the machine frame 2. As in the embodiment according to FIG. 1, the connection carrier 8 is composed of the carrier base body 28 and the drive means 12 which form a longitudinal section 14 of the connection carrier 8 and are detachably connected to one another by means of connection means 23. The drive means 12 at the end portion of the connecting member 8 contacted with a coupling surface 22, the stator 3 and C-stator 5 and is also releasably connected thereto via connecting means 23.
    The drive means 12 has on the pressing beam 9 acting on adjustable and driven drive members 38 which are formed in the case of a drive means 12 in the form of a hydraulic cylinder 13 by piston rods 39. In FIG. 7, the drive means 12 comprises three piston arrangements parallel to one another and lying in the bending plane 32 and accordingly engage three piston rods 39 on the illustrated left end section of the press beam 9. The hydraulic cylinder 13 may also have only a single piston assembly, the generation of the required driving forces by means of several piston arrangements allows An * driving means 12 with low expansion perpendicular to the bending plane 32, whereby a space required for the forming of large workpieces free space is as little as possible.
    An advantageous, optional embodiment of this connection of the press beam 9 on the drive means 12 may be that with the drive means 12, here with the drive members 38 and the pressing bar 9, firmly connected, articulated bending elements 40 are provided, whereby the pressing bar 9 a slight pivotability obtained relative to the drive means 12 about a right angle to the bending plane 32 pivot axis. In FIG. 7, a bending element 40 is formed such that two lateral notches 41 are respectively arranged at the lower end of the piston rods 39, wherein the notches 41 extend at right angles to the bending plane 32. As a result of this weakening of the cross section of the bending element 40 at the end of the piston rod, the bending element 40 functions as a joint and no high and thus harmful bending moments are transmitted to the drive members 38 or the piston rods 39 in the event of a permanent bending of the press beam 9.
    As shown in FIG. 7, a releasable connection of the drive means 12 to the pressing beam 9 can be produced at the ends of the bending element 40 abutting the pressing beam 9 by means of holding elements 42, for example in the form of holding brackets 43.
    In Fig. 7, the bracket 43 are arranged to connect the drive members 38 to the pressing beam 9 at right angles to the bending plane 32, whereby during assembly of the press beam 9 this perpendicular to the bending plane 32 on the ends of the drive members 38, here the piston rods 39, are pushed can. The assembly and disassembly takes place in the embodiment shown in FIGS. 1 and 5 in the lowered position of the press beam 9, in which he is no longer between the plate elements 21 of the connecting member 8 in the central region.
    FIG. 7 also shows an additional possible embodiment variant for the guide 10 of the press beam 9 on the machine frame 2. The guide 10 includes guide rails 11 on the stand 3 and additional guide rails 44 which are attached to the drive means 12. Advantageously, the guide rails 11 and 44 lie in the bending plane 32, whereby the pressing bar 9 brings on the guide 10 no or only slight tilting moments. In the illustrated embodiment, the guide rails 44 are arranged between the two the carrier base body 28 forming plate members 21 and the pressing bar 9 is thereby guided at its enlarged central region.
    In order to achieve an exact guidance of the press beam 9, this guide shoes 45, which comprise the guide rails 11, 44 approximately free of play. N2011 / 26000 -19-
    In this embodiment of the guide 10, the pressing beam 9 is guided in four points, these four points being guided along straight lines formed by the guide rails 10, 44. Since the pressing beam 9 in the illustrated embodiment has a large height, and 9 may result in a forming process due to the deflection of the press beam 9 different changes in length at the guide points, also shown in Fig. 7 extending in the longitudinal direction of the press bar 9 length compensation guide 46 for be provided the guide shoe 45.
    The guide 10 can thus comprise guide rails 11 on the uprights 3, 4 as well as additional guide rails 44 on the connection support 8, which can be arranged on the drive means 12 and / or on the carrier main body 28.
    Fig. 8 shows a partial view of a further possible embodiment of the connection of the press beam 9 on the drive member 38 of the drive means 12, wherein here another embodiment of the bending element 40 is shown, with a slight angular mobility between the drive member 38 and the pressing bar 9 is achieved and thereby at a possible bending of the press beam 9 no the drive means 12 possibly damaging bending moments are introduced into the drive member 38. The bending element 40 is formed in this embodiment on the pressing beam 9 itself by 9 two facing L-shaped recesses 48 are provided on the upper side 47 of the press beam, between which there is a reduced residual cross-section, which causes increased deformability and thus bending mobility. As a holding element 42 between the drive member 38 and the pressing bar 9 can serve in this embodiment, a screw member.
    9 shows a view of a further, possible embodiment of a press brake 1 according to the invention with an alternative embodiment of the machine frame 2. The stands 3 and 4 designed as C-stands 5, 6 carry the connecting support 8 with the drive means 12 and the pressing bars 9 , are essentially made up of two main parts. The connecting support 8 is supported by load stands 49, which are also known as power frames.
    N2011 / 260DD -20- can be drawn, since the force flow from the press table 7 to the connection carrier 8 and subsequently via the drive means 12 to the press beam 9 is produced via this. These substantially C-shaped load stands 49 are bent slightly at high forming forces due to the inevitable, elastic deformations, whereby the connection carrier 8 undergoes a slight posi tion and angle change. The guide 10 for the pressing beam 9, however, is arranged on a separate guide stand 50, via which no forming forces must be transmitted and therefore can hold the guide rails 11 of the guide 10 even with large forming forces in an exact largely unchanged position. In Fig. 9, the guide post 50 is made in two parts and lies in the same plane as the load stand 49, wherein a part is located within the load stand 49 and a part outside the load stand 49 and the two parts are connected by arranged parallel to the stator level plates, the in Fig. On the left C-stand 5 for the purpose of representation of load stand 49 and guide post 50 are not shown.
    The inevitably occurring at large forming forces, different deformations of load stand 49 and guide post 50 would cause tension in the connection between the acting on the load stand 49 drive means 12 and guided on the guide post 50 pressing beam 9, however, can be avoided that between the attachment point 16th and the middle part 17 of the load stand 49, a deformation section 18 is provided, which eliminates or reduces the rigid connection of the connection carrier 8 with the rest of the load stand 49 in such a way that even with a bending of the load stand 49, an angle equalization of the connecting carrier 8 with the drive means 12th can be done to the guide 10.
    This also makes it possible to guide the pressing beam 9 not only on the guide stand 50, but also in addition to the connecting support 8, as already described with reference to FIG. 7. By such a deformation region 18, as has already been described with reference to the embodiment of FIG. 1, even at high forming forces and associated deformations of the machine frame 2 allows only very small internal tension between the
    N2011 / 26000 -21 -
    Drive means 12 and the pressing bar 9, whereby the drive means 12 and the guides 10 are charged much less.
    FIGS. 10 and 11 show in sectional views in the region of the drive means 12 possible variants of the connection carrier 8.
    In Fig. 10, the carrier base body 28 is formed by an I-beam 51 which is so disengaged in the region of the drive means 12 that here only the upper flange 29, the drive means 12 bridges. This embodiment substantially corresponds to the embodiment of a connection carrier 8 shown in FIG. 3.
    Fig. 11 shows a possible embodiment of the connecting carrier 8, in which the carrier base body 28 is designed as a U-profile, in which the drive means 12 is inserted at the open bottom. Due to the not shown, detachable connection of the drive means 12 with the carrier base body 28 and the stator 3, 4 this is despite a continuous support base body 28 is a supporting part of the connection carrier. 8
    In a modification of the embodiment according to FIG. 11, the carrier base body 28 could furthermore be designed as a T-profile with a downwardly projecting central web and in turn comprise two parallel and spaced plates which in the raised position of the press beam 9 between them the central web receive the carrier body 29.
    10 and 11 show that the drive means in the respective longitudinal section 25 (see FIG. 3) forms the predominant portion of the carrier cross-section 27.
    FIG. 6 also shows features of additional embodiments of the press brake 1 which may be provided additionally or alternatively to the embodiments described above.
    The deformation range 18 can also be formed in such a way that the attachment point 16 of the connecting carrier 8 is arranged with the stator 3, or the C-stator 5 in a region of the stator 3 with a relatively small deformation stiffness. For this, the C-stand 5 may be e.g. without a recess 19 N2011 / 26000 wm wsfflm -22- or slit 20 be executed, but at the height that the lower end of the illustrated slot 20 extend horizontally to the rear, as indicated by a dashed line shown at this level upper edge.
    Furthermore, in one embodiment of the C-stand 5 with a slot 20, an actuator 51 acting on both sides of the slot can be provided, with which the widening of the slot 20 can be actively influenced. This can consist in an active enlargement, a reduction or a limitation of the expansion. As a result, the orientation of the connecting carrier 8 can be actively influenced and in particular adapted to the bending plane 32.
    12 shows yet another possible embodiment of the guide 10 of the press beam 9 on the lateral uprights 3, 4. The guide shoes 45 cooperating with the guide rails 11 are fastened by means of hinge elements 53 to the end faces 52 of the press beam 9, whereby upon deflection of the press beam 9 no harmful moments are introduced into the guide 10. Since the pressing beam 9 undergoes an extension at a deflection above its neutral fiber 54 and a shortening below the neutral fiber 54, it is advantageous if, as shown in FIG. 12, the hinge elements 53 are arranged at the level of the neutral fiber 54 In this case, no additional tensile or compressive forces acting in the longitudinal direction of the beam are introduced into the uprights 3, 4 by means of a press beam deflection. The joint elements may be designed as conventional joints with a pin-shaped joint axis or as a bending joint, similar to the previously described bending elements 40 for connecting the press beam 9 to the drive means 12th
    The embodiments show possible embodiments of the press brake 1, 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 possibility of variation due to the teaching of technical action representational invention in the skill of those skilled in this technical field. Thus, all possible embodiments which are possible by combinations of details of the embodiment variant shown and described are also included within the scope of protection.
    Furthermore, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or identical component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or the same 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 are to be transferred to the new situation mutatis mutandis when a change in position. Furthermore, individual features or combinations of features from the different exemplary embodiments shown and described can also represent independent, inventive or inventive solutions. All statements on ranges of values in the description of the present invention should be understood to include any and all sub-ranges thereof, e.g. the indication 1 to 10 should be understood to include all sub-ranges, starting from the lower limit 1 and the upper limit 10, i. all sub-ranges 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.
    For the sake of order, it should finally be pointed out that, for a better understanding of the structure of the press brake 1, these or their components have been shown partly unevenly and / or enlarged and / or reduced in size.
    The task underlying the independent inventive solutions can be taken from the description.
    Above all, the individual in Figs. 1; 2; 3; 4; 5; 6; 7; 8th; 9; 10; 11; 12 embodiments form the subject of independent solutions according to the invention. The relevant objects and solutions according to the invention can be found in the detailed descriptions of these figures.
    N2011 / 26000 i
    List of references 1 Press brake 36 2 Machine frame 37 3 Stand 38 4 Stand 39 5 C-stand 40 6 C-stand 41 7 Pressing table 42 8 Connecting bracket 43 9 Pressing bar 44 10 Guide 45 11 Guide rail 46 12 Drive means 47 13 Hydraulic cylinder 48 14 Longitudinal section 49 15 Middle section 50 16 attachment point 51 17 middle part 52 18 deformation section 53 19 recess 54 20 slot 21 plate element 22 coupling surface 23 connecting means 24 adjustment direction 25 longitudinal section 26 section 27 carrier cross section 28 carrier main body 29 upper flange 30 end fleece 31 longitudinal middle plane 32 bending plane 33 auxiliary carrier 34 connecting means 35 bolt
    cross-section
    cross-section
    drive member
    piston rod
    flexure
    notch
    retaining element
    Bracket Guide rail Guide shoe Longitudinal compensation guide
    top
    recess
    Load stand guide stand
    Actuator end face joint element neutral fiber
    权利要求:
    Claims (23)
    [1]
    1. press brake (1) comprising a machine frame (2), a fixed to this fixed press table (7), one on a guide (10) on the machine frame (2) in a straight line towards the press table (7) adjustably mounted press bar (9 ) and at least one drive means (12) acting on the press beam (9) and on the machine frame (2), the machine frame (2) comprising at least two stands (3, 4), in particular transversely to one from the press table (7) to the press beam (9 ) extending extending bending plane (32) arranged flat C-stand (5, 6) or O-stator, and a two adjacent stand (3, 4) connecting connecting carrier (8), characterized in that at least one longitudinal portion (14) of the connecting carrier (8) or in at least one longitudinal section (25) a predominant portion of the carrier cross-section (27) forming part section (26) of the connecting carrier (8) by the drive means (12) is formed and this with a Trägergr and body (28) of the connecting carrier (8) is detachably connected.
    [2]
    2. Press Brake (1) according to claim 1, characterized in that the drive means (12) formed longitudinal portion (14) or portion (26) at one end portion of the connecting carrier (8) is arranged and has a coupling surface (22) one of the stands (3, 4) contacted.
    [3]
    3. press brake (1) according to claim 1 or 2, characterized in that the one subsection (26) of the connecting carrier (8) forming the drive means (12) on the said pressing bar (9) facing side of the connecting carrier (8) is arranged and the Carrier base (28) on the side facing away from the pressing beam (9) side has a drive means (12) bridging upper flange (29). N2011 / 26000 -2- -2- 10201250566 Sprint ^: ¢) 7-12-20 ^ 2
    [4]
    4. press brake (1) according to one of the preceding claims, characterized in that the stands (3, 4) in the form of C-stands (5,6) are formed, wherein the connection carrier (8) to the bending plane (32) facing top ends of the C-stands (5, 6) and in each case between the attachment point (16) for the connection carrier (8) on the C-stand (5, 6) and a central part (17) of the C-stand (5, 6) is formed a deformation portion (18) with a locally reduced stator stiffness.
    [5]
    5. press brake (1) according to claim 4, characterized in that between the attachment point (16) at the upper end of the C-stand (5, 6) and its central part (17) arranged deformation portion (18) from the upper edge of the C -Ständers (5, 6) outgoing approximately parallel to the bending plane (32) extending recess (19), in particular a parallel to the bending plane (32) slot (20).
    [6]
    6. press brake (1) according to claim 5, characterized in that in the region of the recess (19) of the cross section (36) of the C-stand (5, 6) opposite thereto adjacent cross-sections (37) is reduced by at least one third.
    [7]
    7. press brake (1) according to claim 5 or 6, characterized in that on the recess (19) in the form of a slot (20), an actuator (51) for actively influencing the expansion of the slot (20) is provided.
    [8]
    8. press brake (1) according to one of claims 4 to 7, characterized in that the attachment point (16) for the connection carrier (8) on the C-stand (5, 6) has a greater distance to the press table (7) than the reduced Cross section of the deformation region (18) on the C-stand (5, 6). 06-1.2-2012 N2011 / 26000-3- Printed: 07-12 ^ 2012 ^ 02012/50566
    [9]
    9. press brake (1) according to one of the preceding claims, characterized in that the guide (10) for the pressing beam (9) with the bending plane (32) aligned guide rails (11).
    [10]
    10. press brake (1) according to one of the preceding claims, characterized in that the guide (10) for the pressing beam (9) on the connecting support (8), in particular on the drive means (12), arranged guide rails (44).
    [11]
    11. A press brake (1) according to any one of the preceding claims, characterized in that the connection carrier (8) comprises two to the stand (3, 4) releasably subsequent drive means (12) and a releasably arranged between these central portion (15).
    [12]
    12. press brake (1) according to one of the preceding claims, characterized in that the carrier base body (28) of the connecting carrier (8) comprises two mutually distanced, to the bending plane (32) parallel plate elements (21).
    [13]
    13. press brake (1) according to claim 12, characterized in that the pressing bar (9) is positioned at its upper end position at least partially between the plate elements (21) of the connecting carrier (8).
    [14]
    14. A press brake (1) according to any one of the preceding claims, characterized in that parallel to the connection carrier (8) of this two stands (3, 4) connecting auxiliary carrier (33) is arranged and longitudinal sections (14) and / or sections ( 26) and / or a carrier base body (28) of the connecting carrier (8) by means of connecting elements (34) on the auxiliary carrier (33) can be fastened. 28/40 06-12-2012 IM2D11 ^ 6000 -4- Printed: 07-12 ^ 2012 102012/50566
    [15]
    15. A press brake (1) according to any one of the preceding claims, characterized in that between the Antriebsmitte] (12) and the pressing bar (9) with a drivable and adjustable drive member (38) of the drive means (12) and the pressing bar (9) firmly connected, articulated bending element (40) is arranged, which causes a pivotability of the press beam (9) relative to the drive means (12) about a bending plane (32) right-angled pivot axis.
    [16]
    16. A press brake (1) according to claim 15, characterized in that the bending element (40) is arranged at the end of the drive member (38) and at right angles to the bending plane (32) extending notches (41), preferably in the press bar (9). arranged holding elements (42), in particular bracket 43) engage.
    [17]
    17. A press brake (1) according to any one of the preceding claims, characterized in that the drive means (12) at least two mutually, and in particular to the bending plane (32) arranged in parallel and on the pressing bar (9) engaging drive members (38).
    [18]
    18. A press brake (1) according to one of the preceding claims, characterized in that the connection carrier (8) is at least partially symmetrical with respect to a bending plane (32) parallel longitudinal center plane (31) of the connection carrier (8).
    [19]
    19. A press brake (1) according to any one of the preceding claims, characterized in that the longitudinal center plane (31) of the connection carrier (8) in the bending plane (32).
    [20]
    20. A press brake (1) according to any one of the preceding claims, characterized in that the adjustment direction (24) of the at least one drive means (12) in the longitudinal center plane (31) of the connecting carrier (8). 29/40, 06-12-2012 N2D11 / 26000 -5- -5- 1102012/50566 Printed: 07-12-2012
    [21]
    21. A press brake (1) according to any one of the preceding claims, characterized in that the machine frame (2) at least two the connecting carrier (8) carrying load stand (49) and two of these different, the guide (10) for the pressing beam (9). comprising guide posts (50).
    [22]
    22. A press brake (1) according to any one of the preceding claims, characterized in that the pressing bar (9) at its opposite end faces (52) with guide rails (11) on the machine frame (2) cooperating guide shoes (45) by means of a joint element ( 53) are attached to the pressing beam (9).
    [23]
    23. A press brake (1) according to claim 22, characterized in that the hinge elements (53) in the height of the neutral fiber (54) of the press bar (9) are arranged, based on a deflection in the adjustment direction (24) of the press bar (9). , 30/40 06-12-2012 N2011 / 26000
    类似技术:
    公开号 | 公开日 | 专利标题
    DE3734390C2|1993-10-28|Composite for formwork
    AT504640B1|2008-07-15|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
    EP2768662B1|2018-10-10|Press
    EP2928680B1|2017-01-25|Press brake
    AT515153B1|2015-08-15|bending machine
    AT507110B1|2012-11-15|PRESS TO REFORM MATERIAL
    DE1237409B|1967-03-23|Device for welding, in particular arc welding, of supports made of sheet metal
    EP3037250A2|2016-06-29|Machine frame for a roller press
    EP3077133B1|2017-09-13|Bending press
    EP2814627B1|2016-04-20|Bending press with adjustable beam element
    EP1941956B1|2009-05-20|Bending press for bending a plate in the manufacture of a pipe
    DE3434470A1|1985-04-11|BENDING PRESS
    DE102007063653B4|2011-01-27|Injection molding machine with protective cover
    WO2018234136A1|2018-12-27|Arrangement of guide rails
    EP3699112B1|2021-10-06|Warehouse, especially shuttle warehouse
    EP2477820B1|2014-01-22|Support assembly for an ink-jet printing device
    AT523965A1|2022-01-15|Bending device with deflection compensation
    EP0557745A1|1993-09-01|Divided loom
    WO2021151571A1|2021-08-05|Rolling device
    WO2011026777A1|2011-03-10|Elevator system having a counterweight
    DE2704684A1|1978-08-10|LEVELING MACHINE FOR LEVELING PLATES AND FLAT MATERIALS
    EP0484781A2|1992-05-13|Slab upsetting press for hot wide strip rolling mills
    EP0624441A1|1994-11-17|Frame press
    DE102006047108A1|2008-04-03|Bending machine for sheet material has bending jaw comprising tool support jaw and carrier jaw with support bearings and flexure-limiting components
    DE2914790A1|1979-10-18|ALIGNMENT DEVICE FOR VEHICLE BODY
    同族专利:
    公开号 | 公开日
    EP2928680A1|2015-10-14|
    EP2928680B1|2017-01-25|
    AT513150B1|2014-02-15|
    WO2014085840A1|2014-06-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2678078A|1950-05-24|1954-05-11|Cyril Bath Co|Combined bending brake and press with retractable ram brackets|
    EP0392795A2|1989-04-10|1990-10-17|Yamazaki Mazak Kabushiki Kaisha|Die exchange apparatus for the use of a press brake|
    EP2060387A2|2007-11-19|2009-05-20|Murata Machinery, Ltd.|Press machine and method for controlling a press machine|
    EP2210681A2|2009-01-27|2010-07-28|Trumpf Maschinen Austria GmbH & CO. KG.|Bending press with a multi-part press bar|
    EP2246131A1|2009-04-29|2010-11-03|Trumpf Maschinen Austria GmbH & CO. KG.|Bending press with additional flanges|
    CH411755A|1964-04-24|1966-04-30|Beyeler Willy|Sheet metal bending press|
    DD148323A1|1979-12-27|1981-05-20|Wolf Claus Dieter Dr Ing|PRESS RELEASE IN C STANDARD VERSION|
    IT1224044B|1988-12-29|1990-09-26|Prima Ind Spa|PRECISION BENDING PRESS FOR LONG SHEET PIECES|
    DE4138285C2|1991-11-21|1994-04-07|M & S Brugg Ag Brugg|Hydraulic press brake|
    JP2540450B2|1994-08-17|1996-10-02|日清紡績株式会社|Pressing machine with C-frame structure|
    JPH11226796A|1998-02-13|1999-08-24|Komatsu Ltd|High precise c type frame press|
    AT413340B|2000-02-03|2006-02-15|Trumpf Maschinen Austria Gmbh|MANUFACTURING EQUIPMENT, IN PARTICULAR BUTTING PRESSURE|
    AT427830T|2003-02-26|2009-04-15|Bystronic Laser Ag|METHOD FOR CORRECTING A BENDING AND BENDING PRESSURE|
    AT509239B1|2009-12-17|2013-03-15|Trumpf Maschinen Austria Gmbh|DRIVE DEVICE FOR A BEND PRESS|AT516493B1|2015-02-25|2016-06-15|Trumpf Maschinen Austria Gmbh & Co Kg|press brake|
    AT516718B1|2015-05-18|2016-08-15|Trumpf Maschinen Austria Gmbh & Co Kg|bending machine|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50566/2012A|AT513150B1|2012-12-06|2012-12-06|press brake|ATA50566/2012A| AT513150B1|2012-12-06|2012-12-06|press brake|
    PCT/AT2013/050233| WO2014085840A1|2012-12-06|2013-12-04|Press brake|
    EP13820717.0A| EP2928680B1|2012-12-06|2013-12-04|Press brake|
    [返回顶部]