奥地利专利AT512174A4 BENDING COMPRESSION WITH ADJUSTABLE BEAM ELEMENT

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专利摘要:
The invention relates to a bending press (1) comprising a fixed table (3), an adjustable pressing beam (5), mutually opposite supporting surfaces (9, 10) on the table (3) and on the pressing beam (5) for bending tools (11, 12 ) and an adjusting device (20) on the table (3) or on the pressing beam (5) for adjusting a support surface (9) between a substantially planar and a cambered course (19), wherein the support surface (9) of a beam element (14) the table (3) or the press beam (5) is formed, which is supported by a support structure (19) of the table (3) or press beam (5). According to the invention, the support structure (19) has at least one support element (22) which can assume a helix angle (23) with respect to the adjustment direction (21) of the press beam (5), and the adjustment device (20) comprises a transverse direction to the adjustment direction (21st) ) on the support structure (19), in particular the support member (22) acting actuator (24), with the helix angle (23) of the support member (22) within the table (3) and / or press bar (5) is variable.
公开号:AT512174A4
申请号:T1822012
申请日:2012-02-13
公开日:2013-06-15
发明作者:
申请人:Trumpf Maschinen Austria Gmbh；
IPC主号:

专利说明:

-1 -
The invention relates to a bending press as described in the preamble of claim 1.
When reshaping workpieces with relatively large dimensions, the problem often arises, in particular when folding, that the pressing beam of a bending machine bends due to high forming forces and curved workpieces have non-uniform bending angles along the forming edge. In addition to the ability to increase the rigidity of the forming forces receiving components, other approaches are already known to reduce the adverse effects of machine deformation.
From WO 01/43896 A1 a press brake for producing bent-formed workpieces is known, comprising a fixed to a machine frame angeord-Neten table beams, a relative thereto by means of a drive assembly and in guide assemblies on the machine frame adjustable pressing beam and at opposite support surfaces of the table beam and the press beam arranged tool holders with bending tools. The arranged on the machine frame table joists extending from lateral edges in the direction of the center of the table beam slot-shaped recesses extending over portions of the length of the table beam and in which symmetrically to the center of the table and at their distance simultaneously adjustable spacer elements are arranged. Depending on the positioning of the spacer elements, the table beam above the recesses on a variable deformation resistance and the occurring during a pressing process deflection of the pressing beam center can be compensated by a downward deflection of the ends of the table beam down. N2011 / 03300 -2-
The document US Pat. No. 5,426,966 A discloses a bending press with a stationary table beam and a pressing beam which can be adjusted relative to the table beam by means of drive means. The press beam is formed in two parts, wherein a first beam part is drivingly connected to the drive means and a table beam facing, another beam part is drivingly connected in the region of a central axis via a flexible connecting element with the first beam part. Starting from this connecting element, conically widening slots extend between the first beam part and the second beam part in the direction of the opposite end regions. At the end regions, the slots are provided with wedge-shaped extensions in which spacer elements are arranged to be adjustable perpendicular to a central axis, wherein depending on their position a bending deformation occurring under load of the press beam during a forming process can be counteracted.
From US 4,426,873 A a bending press with a arranged on a support surface of a table beam, a tool holder for the bending tool over an entire length of the press beam extending adjusting device for a variable design of a longitudinal embossment of a footprint for the tool holder is known. The adjusting device is essentially formed by a wedge-shaped in cross-section longitudinal profile, which is divided by cuts in wedge sections and thus has a flexibility in a plane perpendicular to a bending plane extending. By appropriate adjustment of the wedge sections in the plane of a crowning of the support surface of the tool holder for compensating a bending deformation occurring under load of the table beam is achieved on the profile.
Furthermore, from DE 37 09 555 A1 a device is known, are arranged for setting up a pressing tool in a convex state between the lower die and the press table at intervals along the longitudinal direction of the press brake several pairs of upper and lower wedges. A coordinated displacement movement of the wedges is achieved via a resilient spring element which can be acted upon by a control drive and extends over the entire length of the press brake. The elastic spring element extends, with which a bearing surface for the tools or a receiving device for the tools occupies a vault that is tailored to the requirements and thus compensation for the bending of the table beam and / or press beam over an entire bending length is achieved and thus the depth of insertion of the bending tools over the entire bending length approximately equal is. However, the production of the wedge pairings and the displacement mechanism is structurally very complex.
The object of the invention is to provide a bending press in which a support surface for bending tools on a press table or pressing beam in a structurally simple embodiment in its course is actively changeable. The object of the invention is achieved by a generic bending press with the characterizing features of claim 1.
Characterized in that the support structure comprises at least one elongate support member which can take at least partially a helix angle with respect to the adjustment of the Pressbaikens, and the adjusting device comprises a transversely acting to the adjustment on the support structure, in particular the support member actuator, with the helix angle of the support element can be changed within the table and / or press beam, it is possible to optimally adjust the course of the support surface to the deflections caused by the deformation of the bending press, whereby uneven degrees of deformation of the workpiece and thereby caused geometric errors can be substantially reduced. Such support elements are very simple components and the manufacturing cost of such a bending press is relatively low. The adjustment can be made so that the helix angle is increased by the actuator either on the basis of an initially not existing skew or relatively small skew or is reduced starting from an initially existing skew. The helix angle of a support element can therefore be present either before the adjustment by the actuator or only after the adjustment by the actuator. N2011 / 03300 • ♦ · ♦ -4-
The oblique portions of the support member cause a greater elastic mobility and it can be relatively easily adjusted using the actuators, the oblique division and thus the crown height of the support surface. The desired course of the support surface can be adjusted before the start of a forming process, but the design of the actuator allows an active adjustment of the curve even during a forming process. As actuators here are systems that correspond to the drive means of the press beam so for example hydraulic cylinders or servomotors with adjusting spindles. Thus, the existing press control can be easily supplemented by the control of the actuators. The angular displacement of the at least one support element by the at least one actuator and the resulting curvature of the support surface can be adapted to the deflection of the press beam in various ways. So it is possible, for example, that the expected maximum forming force is calculated in advance and based on a determined in experiments series between forming force and Pressbalkendurchbiegung the required curvature of the support surface and thus the required angular displacement of the support element before reaching the maximum forming force or even before the start of forming is made. Alternatively, it is also possible that by means of suitable sensors, e.g. Strain gauge or the detection of the current forming force, e.g. via the hydraulic pressure or the drive current strength of the drive means, which is measured or calculated in a forming process currently occurring deflection of the press beam and the pressing table by adjusting the support member during the forming process is set to the respective current value of the deflection corresponding curvature of the support surface active.
The at least one support element is not only actively adjusted by the actuator in its helix angle, it is also possible during a bending operation to use the actuator in such a way that an unwanted deformation of the beam element by the forming forces and thereby caused too strong spring back of a support member by the Aktuatorkraft counteracted.
The actuator preferably has a holding function with which e.g. a retraction of a hydraulic piston can be blocked or a parking brake. It is possible that the actuator counteracts an undesired deformation of the support structure by means of a position control and a controlled increase in the actuating forces.
Preferably, the respective deformation state of the press beam, preferably also the support structure by means of suitable sensors, e.g. Strain gauges are detected and based on the corresponding activation of the actuators done.
If the support structure comprises a plurality of inclined support elements, the beam element can be actively changed at a plurality of support points and the curve of the support surface can be more uniform. The adjustment of the support elements can be effected by means of an actuator, but preferably by a plurality of actuators, whereby the adjustment movements of the individual support elements can be varied and independent of each other influenced. By means of a plurality of support elements, it is further possible to optimally compensate for asymmetrical deflections of the press beam, which can occur in off-center bending operations, by means of a corresponding asymmetrical adjustment of the support elements. The required curvature or crowning of the support surface can be made to match a pre-calculated or measured during the forming process directly or indirectly measured deflection of the press beam.
The support elements of a support structure may also be formed from a plurality of spring plates, which are provided in a corresponding number and with corresponding cross sections. The spring plates can be connected with their ends relatively rigid or even relatively articulated to the beam member or a base member. A rigid version of the attachment may e.g. in that the ends are inserted in grooves or slots which extend horizontally and transversely to the adjustment of the adjustable pressing beam.
Preferably, the helix angles of all inclined support elements lie within a plane and parallel to the adjustment plane of the press beam. The adjustment movements can thereby also take place within a plane, which is constructive in the case of a N2011 / 03300 elongated beam element is easier and the depth of the press table o-the bar is not significantly increased by the actuators and support elements. Due to the arrangement of the helix angles in one plane, the adjustment forces of the actuators are also essentially in one plane, and a plurality of support elements can be adjusted in a simple manner by means of an actuator.
In order to avoid undesirable deflection of the oblique support elements transversely to the adjustment plane of the press beam, it is advantageous to guide them between two parallel to the adjustment plane of the press bar guide plates or aprons with little play. The requirements for the rigidity of the support elements transversely to the adjustment are thereby lower. Further, by the guide plates, the rigidity of the beam member can be increased when these are fixedly connected to beam member e.g. are bolted, whereby the beam element point loads, resulting from bending operations on short tool stations can provide sufficient rigidity and no local deformations occur.
To further increase the guide plates or aprons may be connected to each other at their spaced from the beam element edges by means of a lower chord or with a arranged from the beam element after the support element base element fixedly connected, which as well as a lower flange, the rigidity of the beam element can further increase local deformations due to punkartiger loads during bending operations are avoided.
Increased elasticity and thus easier adjustability of the support elements is achieved if a longitudinal dimension of the at least one support element in its direction of support at least three times its Querschnrttab measurement in parallel to the beam element element.
In order to avoid forces acting in the longitudinal direction of the beam element, it is advantageous if, between the support element and the beam element or between the support element and the base element, which forms the fixed part of the support structure, a displacement bearing movable in the longitudinal direction of the beam element N2011 / 03300 * * «I φ * t is formed. The second variant is provided if the actuator engages the distanced from the beam element end of the support element. For the common designs of press beams with symmetrical arrangement of the drive means and symmetrical arrangement of the guides on the machine frame, it is advantageous if the support elements and the actuators are arranged symmetrically with respect to a rechtwinkeiig to the longitudinal axis of the beam element extending center plane of the press brake.
An easily manufactured and particularly stable embodiment of a support structure can be produced when a plurality of adjacent support elements are formed by inserted in a plate-like base member of the table or the press beam te slanted slots, the slots completely pass through the base member. These slots can be introduced, for example, by laser cutting economically and flexibly modifiable.
The course of the support surface, which arises upon activation of the actuators, can also be adapted to the deformation behavior of the press beam by the support structure comprises a plurality of obliquely extending support elements with different sized cross-sectional areas and / or the support structure a plurality of inclined support elements with respect to the adjustment different Includes helix angles. A locally stronger adjustment of the beam element at the same adjustment of the actuator can be achieved by a arranged in this zone support member with a larger helix angle. Support elements with smaller cross-sectional areas have a higher elasticity and can be provided there where a greater compliance of the beam element is desired. For bending presses in which the drive means for the forming process engage the end sections of the press beam, it is advantageous if the helix angles of support elements in the middle section of the beam element are greater than those of support elements positioned closer to the end sections, since in this most common drive form of a press beam the crowning of the support curve in the middle is most needed and this can be achieved by the central larger helix angle, even if the same horizontal adjustment path is impressed on all support elements.
A simple production of a beam element and calculation of the curve and the required adjustments of the support elements is possible if the beam member has a substantially constant bending stiffness over its entire length.
A good relationship between sufficient adjustability and sufficient rigidity of the support structure is achieved when the helix angle of the support member or the support elements with respect to the adjustment is between 0 ° and 45 °, wherein the effect according to the invention can be realized in a support element oriented in the adjustment that this is moved from the vertical base position by the actuator in an oblique position, whereby the beam element can be locally lowered or raised. Larger helix angles result in an unfavorable force transmission, if the force introduction direction of the actuator is approximately in the horizontal direction, but a stronger vertical adjustment of the supported beam element. For small helix angles, however, a good force transmission or a toggle effect can be achieved.
If adjacent support elements are oriented obliquely oriented in the same direction within a subsection of the beam element, a larger number of support elements can be accommodated on a short subsection of the beam element than in the case of alternating orientation.
A largely smooth course of the support surface and an avoidance of force in the longitudinal direction of the beam member is achieved when the support member or the support elements is formed with respect to a direction perpendicular to Versteiligkeit symmetry plane in the form of a herringbone pattern substantially symmetrical with two opposite in relation to the adjustment direction of the press beam inclined sections or are and the force introduction direction of the actuator or the actuators substantially in the plane of symmetry of Stützele- N2011 / 03300
ment lies. By substantially mutually parallel support elements within such a structure, a large number of adjustable support elements can be accommodated in a small space. The individual support elements in this case have to absorb only a small portion of the forming forces and can have smaller cross sections.
An alternative embodiment having similarly advantageous effects results when the support structure comprises a plurality of support wires formed from support elements with oblique support sections and the force introduction direction of the actuator lies substantially in the plane of symmetry of the support rails perpendicular to the adjustment direction.
If in each case a separate actuator is provided between adjacent support rods, horizontal displacements of the connection points on the beam element or on the base element can be prevented and a displacement bearing at the upper and lower ends of the support elements can be dispensed with here.
A simple embodiment of a support structure results when at least one oblique support element connected to the actuator is arranged in the middle section of the beam element and the support structure at the end sections of the beam element has a higher rigidity in the adjustment direction than the oblique support element not force-urged by the actuator. For applications in which a workpiece is bent in the middle section beam element, this simple construction, the harmful deflection of the press beam can be largely compensated.
An embodiment with also a low number of support elements may consist in that at least two oblique support elements connected to an actuator are arranged at the end portions of the beam element and the support structure in the center portion of the beam element has a higher rigidity in the adjustment direction than the oblique ones not force-urged by the actuators support elements. N2011 / 03300 10
To avoid or reduce bending moments and multiaxial stress states within the support structure, it is advantageous if the at least one support element is mounted with at least one end on the beam element, on the support structure, on the table or on the pressing beam by means of a joint or bearing. In particular pivot bearings or slide bearings can be used as joints.
The number of components required for a support structure is reduced if the at least one support element is integrally formed with at least one end on Bal-kenelement, on the support structure, the table or on the pressing beam.
The number of actuators can be reduced or kept low even when installing a plurality or many support elements by a support element or more support elements with an actuator only indirectly with the interposition of another support member is in connection or stand.
The forwarding of the adjustment forces exerted by the actuators can advantageously take place by means of webs or support elements arranged between adjacent support elements for mutual transmission of force.
In order to be able to adapt the curve of the support surface flexibly to the application of the dependent bending of the press beam, it is advantageous if a plurality of actuators acting transversely to the adjustment on the support elements are arranged in the support structure, which is controlled by a control of the bending press and individually or at least groups can be activated with different adjustment paths.
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:
Figure 1 is an overall view of a bending press with a possible embodiment of an actuating device and support structure for active adjustment of a support surface. N2011 / 03300 - 11 -
Figure 2 is a view of a press table with a possible embodiment of an actuating device and support structure.
3 shows a view of a press table with a further possible embodiment of an adjusting device and supporting structure;
4 shows a detail of a further possible embodiment of a support structure with an angled support element;
5 shows a section of a further possible embodiment of a support structure with supporting elements in the form of a herringbone structure;
6 shows a view of a further possible embodiment of an adjusting device and supporting structure with diamond-shaped support elements;
7 shows a section through a press table with an adjusting device and a support structure shown in FIG. 6; FIG.
Fig. 8 is a view of another possible embodiment of an actuating device and support structure with straight support elements and a sliding bearing to compensate for horizontal displacements of the support elements and
9 is a view of another possible embodiment of an adjusting device and support structure with angled support elements in herringbone structure.
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 are to be transferred to the new situation mutatis mutandis when a change in position. Furthermore, N2011 / 03300 * · * -12-
Represent individual features or combinations of features from the illustrated and described different embodiments of their own, 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 subregions 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.
Fig. 1 shows a front view of a bending press 1 in the form of a press brake, based on which the inventive principle is explained.
The bending press 1 comprises a machine frame 2, with which a fixed table 3 is connected. The machine frame 2 is further supported by means of guide assemblies 4 a vertically adjustable pressing bar 5, wherein the adjustment is effected by drive means 6, for example in the form of hydraulic cylinders. The machine frame 2 comprises in a frequent embodiment two spaced-apart side cheeks 7, for example in the form of C-stands, which are connected by means of transverse connectors 8. At the table 3 and the pressing bar 5 are opposing or mutually facing support surfaces 9 and 10 are formed, on which cooperating bending tools 11 and 12 can be arranged. The bending tools can also be attached by means of their own tool receiving devices, the execution of the bending tools themselves or any adapter or tool holders is not relevant to the subject of the invention.
A common form of the bending tools is an arrangement of a bending die on the support surface 9 of the table 3 and the attachment of a punch on the support surface 10 of the press beam 5. When approaching the press beam 5 to the table 3 can by the cooperating bending tools 11 and 12 N2011 / 03300 -13- ♦ «• t ♦ * • · * · t · ♦ · * ♦ · # * ··« «· • * · · ♦
Forming forces are exerted on an inserted therebetween workpiece 13, whereby this is subjected to a bending deformation.
The support surface 9 on the table 3 is thereby formed by a beam element 14 on the table 3 and the upper support surface 10 by a beam element 15 on the pressing beam 5. The beam elements 14 and 15 extend over the total length 16 of the table 3 or of the press beam 5, whereby the bending tools 11, 12 can be suitably selected and positioned as required by the workpieces 13 to be bent.
As shown in Fig. 1, the forming forces occurring during a pressing process cause a deflection 17 of the press beam, which is problematic especially for long workpieces 13, as along the forming zone, here the bending edge, no uniform degree of deformation is given and therefore an uneven deformation is possible , Thus, with a folded workpiece 13, the bending angles at the outer ends of the bending edge do not coincide with the bending angle in the middle of the bending edge.
In order to prevent or reduce this disadvantageous effect, it is provided in the bending press 1 according to the invention, on the opposite support surface 9 on the table 3 to create a corresponding bow 17 corresponding to the curve 18. This results in a uniform degree of deformation of a workpiece to be bent 3 along the bending edge and a uniform, constant bending moment is achieved in a press brake,
The lower beam element 14 on the table 3 is supported by a support structure 19 of the table 3 and an adjusting device 20 is arranged in the table 3, with which this cambered course 18 of the beam element 14 can be effected. The lower beam member 14 and the upper beam member 15 extend by this measure under the influence of forming forces at a constant distance, with the maximum deflection of the press beam at a total length 16 of the table 3, for example, 2500 mm in the range of a few millimeters, for example a maximum of 3 mm moves The deflection of the press beam 5 with the upper beam element 15 results essentially in the adjustment direction N2011 / 03300 -14- w 21 of the press beam 5 and in the adjustment plane, which corresponds to the plane of the drawing in FIG.
In order to produce such a cambered course 18, the lower beam element 14 must be raised slightly upwards in the middle region upwards against the pressing direction, that is to say in the illustrated embodiment at least at the conclusion of the pressing process or uniform process. The amount by which the lower beam element 14 must be raised can be calculated in advance by a controller in a good approximation, based on the known deflection behavior of the press beam 5, or the corresponding values for the required crowning of the lower beam element 14 can be known on the basis of series of tests on specific load situations be.
The support structure 19 has an elongate support element 22, which has a helix angle 23 with respect to the adjustment direction 21 of the press beam. In order to be able to actively effect a displacement of the beam element 14, the adjusting device 20 comprises an actuator 24, for example in the form of a hydraulic cylinder, with which the helix angle 23 of the support element 22 within the table 3 can be changed. As can easily be seen in FIG. 1, a reduction in the helix angle 23 causes the beam element 14 to lift, causing the cambered profile 18 to be effected.
In Fig. 1, for the sake of simplicity, only an inclined support member 22 is shown, which acts as a simplified point load from below on the beam member 14; However, in order to obtain a continuous and the deflection 17 of the press beam 5 corresponding cambered course 18, advantageously, a plurality of oblique support members 22 may be provided, the helix angle 23 by means of at least one actuator 24 can be changed. The support element 22 is at least slightly displaceable due to its elongated design within the support structure 19, and the elongate embodiment is to be understood such that a longitudinal dimension of the support element 22 is greater than its dimension transverse to its longitudinal axis and in the direction of its minor extension. N2011 / 03300 15- • «* · · ♦ · * ···« * ♦ · · · »i ·«
Overthrust. Preferably, the longitudinal dimension of the support element 22 is more than three times its cross-sectional dimension in the longitudinal direction of the beam element 14.
The actuator 24 acts in the illustrated embodiment directly on the support member 22 and in turn is supported on the rest of the support structure 19, which can be considered in the illustrated embodiment in comparison to the support member 22 as rigid and immovable. That part of the supporting structure 19, on the table 3 or on the pressing beam 5, which can essentially be regarded as rigid, may also be referred to as the base section. The beam elements 14 and 15 are executed in the illustrated embodiment as separate components, but may also be an integral with the table 3 or pressing beam 5 related element. The longitudinal axis 25 of the support member 22 has with respect to the adjustment direction 21 a helix angle of preferably between 10 ° and 45 °, depending on the actual helix angle 23 different effects come to bear more. At a smaller helix angle 23 results in a good power transmission, that is, with relatively little force of the actuator 24, a high biasing force can be achieved on the beam member 14. If a relatively large helix angle 23 is selected, a better movement ratio is achieved, that is to say a small adjustment path on the actuator 24 causes a relatively large, vertical adjustment path for the prestressing of the beam element 14.
The deflection 17 of the beam element 15 during a forming process will in many cases be substantially symmetrical with respect to a longitudinal plane of the beam element 14 perpendicular extending center plane 26 of the bending press 1 and it is therefore advantageous if the adjusting device 20 with the inclined support elements 22 so executed is that the cambered profile 18 of the lower beam member 14 is also effected symmetrically to the center plane 26. 1 shows a very simplified embodiment of a support structure 19 with an obliquely extending support element 22, and different embodiments of support structures 19 are shown in sequence, with which a support structure 19 is inserted transversely to the adjustment direction 21 of the press beam. 03300 - 16 - * actor 24 a cambered profile 18 of a beam element 14 can be achieved.
The use of a support structure 19 with actively adjustable, inclined support member 22 is not limited to a table 3, but can of course also be used on a press bar 5 to a caused by the forming forces bending of the press bar 5 ddddurch an opposite, active deformation of the beam element 15 balance. Accordingly, the foregoing and following embodiments are also for embodiments of bending presses 1 ausgeiegen in which such oblique support members 22 are provided only at the table 3 or only to the pressing bars 5 or both the table 3 and the pressing bar 5.
The support structure 19 includes in certain embodiments as a fixed part next to the adjustable support members 22 1ein plate-like base member 27, as those are also used in known from the prior art bending presses 1 both for the press table and for the pressing beam. However, columnar embodiments of support structures 19 are also conceivable, which likewise include oblique support elements 22 and actuators 24 acting thereon.
An important effect of an oblique support member 22 is the comparatively great mobility in Verstelirichtung 21, which is greater than in support elements, which are arranged parallel to 21 Verstelirichtung. This mobility is used in conjunction with the actuator 24 to bias a beam member 14 accordingly.
The illustrated embodiments of support structures with oblique support members 22 may, as already described, by active reduction of the helix angle 23 a cambered profile 18 of the respective beam element 14 and 15 cause, but it is also possible by actively increasing the helix angle 23, a beam element 14 locally lower or to produce a concave profile 19. This could be applicable, for example, if the upper press beam 5 only comprises a drive means 6 in its central region.
In the embodiment shown in Fig. 1, the lower end of the support member 22 is integrally formed on the base member 27 of the table 3, that is, the support member 22 is elastically deformed upon activation of the actuator 24 relative to the rest of the table 3 and the base member 27 and thereby brought the beam member 14 in the cambered course 18. This deformation of the oblique support member 22 is made possible or substantially facilitated by its elongated embodiment.
FIG. 2 shows a simplified view of a similar embodiment of a support structure 19 on a table 3 or a press beam 5 in a partial view of a bending press 1. In this embodiment, as in the previously described in the central region 28 of the beam member 14 and 15, a sloping support member 22 is arranged, which can be changed by means of an actuator 24 in its helix angle 23. The end portions 29 of the beam member 14 and 15 are supported by a part of the support structure 19, which have a higher rigidity in the adjustment direction 21 at the end portions 29, than the inclined support member 22. The inclined support member 22 arranged in the central region 28, as before described, even by a plurality, such oblique support members 22,22 ', ... be replaced. If the actuator 24 exerts a compressive force to the left, the support element 22 is moved to a steeper position, thereby slightly raising the beam element 14 in its middle region 28. Since this adjustment of the support member 22 shifts its upper end not only in the vertical direction but also in the horizontal direction, it is in such an arrangement of the support member 22 is advantageous if, as shown in Fig. 2, between the upper end of the support member 22 and the beam member 14 a movable in the longitudinal direction of the beam member 14 sliding bearing 30 is formed. With the system shown in Fig. 2 it is also possible to make a concave run 18 ', for example by the actuator 24 pulling the upper end of the support element 22 to the right or to the left of the upper one End of the support member 22 is arranged and increases by applying a compressive force the helix angle 23 of the support member 22, whereby the upper end is slightly lowered.
FIG. 3 shows a partial view of a further embodiment of a support structure 19 for a beam element 14 of a bending press 1. The two end portions 29 of the beam member 14 are supported by obliquely extending support members 22, while the central portion 28 is supported by the rest of the support structure 19 and in the central portion 28 a higher rigidity in the adjustment 21 aulweist, as the inclined support members 22. The two support members 22 can be adjusted by their actuators 24 in their pitch relative to the base portion 27 and with respect to the rest of the support structure 19 in its helix angle 23, whereby the end portions 29 of the beam element 14 can be actively adjusted. Again, depending on the mode of operation of the actuators 24 or their arrangement is possible, as already described with reference to FIG. 2, to achieve a concave or a convex course of the support surface 9 on the beam element 14. Before being adjusted by the actuators 24, the support elements 22 can also have a helix angle of 0 ° with respect to the adjustment direction 21, which can be increased by the actuators 24 and thus the beam element 14, 15 is adjusted.
The variant shown in Fig. 3 could also be modified to the effect that the support members 22 are slidably mounted at its lower end relative to the base element 27 by means of sliding bearings 30 and the actuators for lowering the lateral ends of the beam element 14,15 at the lower end of the support elements 22nd attack and exert compressive forces in the direction of the vertical center plane.
In Fig. 3 is further indicated by dashed lines on the right support member 22 that it can also assume a helix angle of 0 ° in the normal position, which can be increased by the actuator 24, whereby also the course of the support surface 9,10 are actively changed can. N2011 / 03300 • · * ·
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♦ »» * · »# · ···« · • · ·
FIG. 4 shows a detailed detail of a further embodiment of a support structure 19, with which a beam element 14 can be adjusted between a flat and a convex or concave curve by the action of an actuator 24, by a support element 22, which supports the beam element 14 in relation to FIG Rest of the support structure 19 ie the base element 27, the rest of the table 3 or the press bar 5, supported and can be adjusted in its helix angle 23 by the actuator 24.
According to FIG. 4, the support element 22 has two oblique sections 31 and 32, which run obliquely with respect to the adjustment direction 21, wherein the helix angles 23 of the two inclined sections 31 and 32 are in opposite directions with respect to the adjustment direction 21. The support member 22 is thus V-shaped and the two free ends of the V-angle with the beam member 14 and the base member 27 are connected. As shown in Fig. 4, the two inclined portions 31 and 32 of the support member 22 may be connected to each other by means of a hinge 33, as well as the other ends of the inclined portions 31 and 32 may be hinged by means of joints 33 on the base member 27 and the beam member 14. Of course, it is also possible that between the two inclined sections 31 and 32, no joint is formed, but these merge into one another in one piece. Likewise, the connection of the support member 22 may be performed on the base member 27 and the beam member 14 without joint.
The special shape of the support member 22 with two opposing, oblique inclined portions 31 and 32, in which the actuator 24 engages transversely to the adjustment direction 21 in the middle of the support member 22 offers special advantages, since this embodiment of a support member 22 no horizontal relative displacement between the beam element 14 and the base member 27 causes, but only in the upper pivot point a lowering or lifting. In the area of small helix angles, for example below 30 °, this embodiment of a support element 22 also brings about a certain toggle effect, as a result of which large actuating forces can be exerted on the beam element 14 with relatively small actuating forces of the actuator 24. This effect can also be achieved if NZ011 / 03300 *
No own joints 33 are provided or they are arranged only at certain points of the support element 22.
It is advantageous if the two inclined sections 31 and 32 have identical but opposing helix angles 23 and the two inclined sections 31 and 32 have identical lengths, that are substantially symmetrical with respect to a plane perpendicular to the adjustment direction 21 symmetry plane 34 are executed. The actuator 24 is shown in simplified form in FIG. 4 by an arrow, which also represents the optimum force introduction direction, which likewise lies substantially in the plane of symmetry 34 of the support element.
In Fig. 4, for simplicity, only a single support member 22 of a support structure 19 is shown, but it is preferably provided in the various embodiments of a bending press an arrangement of a plurality of support members 22, whereby the required or necessary forces during an adjustment and a bending operation distribute on several support elements 22. Furthermore, the trajectory 18 of the support surface 9 by the use of multiple support elements 22 is more uniform.
5 shows a partial view of a further embodiment of a support structure 19 for a beam element 14 which comprises a plurality of support elements 22 which can be changed in their helix angle 23 by means of an actuator 24 and thereby the beam element 14 is actively raised in the area above the support elements 9 can be lowered. The individual support elements 22 are arranged side by side in the longitudinal direction 35 of the beam element 14 below the beam member 14 and have in this embodiment, similar to the embodiment of FIG. 4 each two inclined sections 31 and 32, with respect to the adjustment direction 21 opposing helix angle 23rd and are arranged and configured substantially symmetrically with respect to a plane of symmetry 34 parallel to the longitudinal direction 35.
Adjacent support elements 22 in this case have an orientation in the same direction, that is, corresponding oblique sections 31 and 32 of adjacent support elements 22 have helical angle oriented in the same direction 23. This N2011 / 03300
Helix angles 23 of adjacent support members 22 may be identical, but it is also possible that the helix angle 23 increases and decreases from one support member 22 and the support portions 31 and 32 to the adjacent support member and the adjacent support portions 31 and 32, respectively. As previously described, causes a larger helix angle 23 at the same adjustment of the actuator 24, a greater height adjustment of the beam member 14, as a smaller helix angle 23, whereby different helix angle 23 allow for the same adjustment of the actuator 24 locally different adjustments of the beam element 14 to achieve.
In principle, each support element 23 can be actuated or adjusted by its own actuator 24, as shown in FIG. 5, but it is also possible that a plurality of adjacently arranged support elements 22 can be adjusted simultaneously by means of a single actuator 24, whereby a small number of actuators 24 a large number of support members 22 can be adjusted.
Adjacent support elements 22 are based in this case in particular in the direction of the introduction of force of the actuator 24 from each other, whereby the adjusting force of the actuator can be introduced into several consecutive support elements 22 at the same time. In Fig. 5, the mutual support of the support members 22 is realized by webs 36 which connect adjacent support members 22 integrally with each other. It is of course also possible that between the individual support elements 22 separate spacers 37 are arranged, as indicated in Fig. 5 by dashed lines. The supporting structure 19, which supports the beam element 14 with respect to the stationary remainder of the table 3 or of the press beam 5, forms in the illustrated embodiment a herringbone structure 38 which makes it possible, by means of a single actuator 24, to make a section or a large part of a beam element 14 very stable to support and simultaneously adjust the support surface 9 between a flat and a curved course. N2011 / 03300 -27- *
The individual support elements 22 may, as in FIG. 4, be designed as separate components which connect the beam element 14 to the base element 27, but the embodiment shown in FIG. 5 is also advantageous in the case of the herringbone structure 38 by integrally connected support elements 22 is formed, which is used as a single contiguous component between Basisefement 27 and beam member 14 or as shown also integrally connected to the base member 27. In Fig. 5 is further indicated that the herringbone structure 38 can also integrally into the beam element 14 'pass over, whereby, for example, the entire table 3 may consist of only one component.
The individual support elements 22 can, as shown in FIG. 5, be produced in such a way that a sequence of inclined slots 39 relative to the adjustment direction 21 is introduced into a plate-like base element 27, whereby the individual support elements 22 or support sections 31 between adjacent slots 32 are formed. These slots 39 can be made for example by laser cutting with relatively little effort. With the help of programmable laser cutting machines such herringbone structures 38 can also be made very flexible and adapted to the requirements of a bending press 1.
FIG. 6 shows a further embodiment of a support structure 19 for a bending press 1 according to the invention; and FIG. 7 shows a cross section through a table 3 of a bending press 1 with a support structure 19 according to FIG. 6.
The support structure 19 in FIG. 6 has a plurality of support rods 40 formed from support elements 22 with inclined sections 31 and 32, which support the beam element 14 either directly or, as shown in FIG. 6, act on the underside of the beam element 14 with the interposition of a transverse connector 41 can.
In the area of the horizontal plane of symmetry 34 of the support grooves 40, the support grooves 40 are mutually supported in the horizontal direction by means of actuators 24, with which also the respective helix angle 23 of the inclined sections 31, 32 N2011 / 03300 can be adjusted and thus the curvature of the beam element 14 are influenced can. The two outer support rods 40 were supported by further actuators 24 relative to the base element 27 of the table 3. In Fig. 6, three supportive rods 40 are shown, but it is also possible that any number of supportive members 40 or a single supportive member 40 is provided. Due to the symmetry of the support grooves 40 with respect to the symmetry plane 34 parallel to the beam element 14 and symmetrical adjustment of the support elements 22 with respect to the adjustment direction 21, the upper and lower connection points of the support elements 22 are not displaced in the horizontal direction and therefore do not produce appreciable forces in the horizontal direction Inter alia, the transverse connector 41, as already described with reference to FIG. 5, also form the beam element 14 '.
The mode of action of these support wires 40 in conjunction with the actuators 24 is similar to that of a scissors jack and can also be achieved here with reference to FIG. 4 described and also in Fig. 5 possible toggle effect.
As actuators 24 preferably hydraulic cylinders are used which represent an optimal solution for the low adjustment path required and high adjustment forces.
In support structures in which larger displacement of the support members 22 are required, the use of spindle drives is possible, in which case preferably a plurality of support members 22 are stiffened by a spindle drive simultaneously, since it would not be economical for each support member 22 to provide its own spindle drive.
In the case of a plurality of actuators 24 acting on the support elements 22 of a support structure 19, it is advantageous if these allow individually adjustable adjustment paths, as this also allows a curve 18 of the beam element 14 adapted to the respective application to be adjusted, which makes possible a deflection 17 of the press beam 5 in the best possible manner compensated. This individual actuation of the actuators 24 can be carried out by a controller 42 shown in FIG. 1, which can be found under N2011 / 03300 ** - 74-
Measured values of the deflection of the press beam 5 as well as measured values of the active deformation of the beam element 14 can also take into account and generate a control of the course 18 of the support surface 9 based on measured values of the deflection of the press beam 5. The control can alternatively or additionally also be based on force measurements on the press beam 5 or on the beam element 4.
FIG. 7 shows a cross section through a table 3 of a bending press 1 according to the invention, wherein a support structure 19 according to FIG. 6 is used. The support structure 19 with the support elements 22 can, as shown in FIG. 7, be guided on both sides by guide plates 43 or aprons parallel to the adjustment plane of the press beam 5, whereby a possible buckling of support elements 22 transversely to the adjustment plane of the press beam 5 can be avoided. The guide plates 43 can cause a substantial increase in the rigidity of the beam member 14 so that no local deformations of the beam element occur at punctual loads by bending operations with short bending edges.
Fig. 7 shows in dashed lines nor the variant that the beam member 14 is fixedly connected to increase the rigidity with the guide plates 43. The guide plates 43 may further be connected to one another at their spaced from the beam member 14 end portions 44 by means of a lower chord 45 with each other, whereby the basic stiffness of the beam member can be further increased. The same effect as a separate lower flange 45 can also cause a fixation at the lower end of the base member 27.
In FIG. 8, a further embodiment of a support structure 19 is shown in simplified form, with which a support surface 9 of a beam element 14 can be adjusted starting from a flat initial state in a convexly or concavely curved course 18. The support structure in this case comprises a plurality of support elements 22, which are arranged symmetrically to a median plane 26 of the bending press and on both sides of the median plane 26 in the same direction oriented helix angle 23 have. The upper ends of the oblique support elements 22 of one half are N2011 / 03300 -25-
is summarized by a cross connector 41 and presses it on the underside of the beam member 14 when the actuators 24 which act in this embodiment on the cross connector 41, are activated. To compensate for the inevitably arising horizontal movement component of the cross connector 41, a displacement bearing 30 is provided between the cross connectors 41 and the underside of the beam member 14, whereby no or no significant horizontal forces are transmitted between the cross connectors 41 and the beam member 14. The sliding bearing 30 is preferably formed by a sliding bearing, which is inexpensive to manufacture and has lower surface pressures than, for example, a rolling bearing.
FIG. 9 shows a further embodiment of a support structure 19, which on both sides of the center plane 26 comprises a herringbone structure 38 which can be adjusted by means of lateral actuators 24 which are arranged in the region of the plane of symmetry 34 of the herringbone structures 38. By lateral pressure forces of the actuators 24, the central portion 28 of the beam member relative to the end portions 29 are raised, thereby to allow optimum adaptation of the support surface 9 to a deflection 17 of the press beam 5. The herringbone structures 38 according to FIG. 9 essentially correspond to those of the embodiments of FIG. 5 or 6. Since all the support elements 22 are adjusted horizontally by the actuators 24 in the region of the plane of symmetry 34, the beam element 14 is raised to a greater extent in the central region 28 must, the support members 22 are disposed in the central portion 28 with a larger helix angle 23 than the outer and the end portions 29 adjacent support members 22 having a smaller helix angle 23 '.
The embodiments show possible embodiments of the bending press, which 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 action by representational Invention in the knowledge of this technical N2011 / 03300 26
Area professional. It is thus also possible to subject all conceivable embodiments, which are possible by combinations of individual details of the embodiment variant shown and described, if appropriate, to new articles of claim.
In the various figures, several and optionally independent embodiments of the bending press are shown, wherein in the figures the same reference numerals or component names are used consistently for the same parts. In order to avoid unnecessary repetitions of the component descriptions, reference is made to the descriptions in the above-described figures.
For the sake of order, it should finally be pointed out that in order to better understand the structure of the bending press, these or their components have been shown partially 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 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 / 03300 Φ Φ Φ · Φ
REFERENCE NUMBERS
Bending press Machine frame Table Guiding arrangement Press beam
Drive center! Sidewall Cross connector Support surface Support surface 36 Bridge 37 Spacer element 38 Herringbone structure 39 Slot 40 Support diamond 41 Cross connector 42 Control 43 Guide plate 44 End section 45 Lower flange
bending tool
bending tool
workpiece
beam element
beam element
total area
deflection
course
support structure
setting device
adjustment
support element
helix angle
Actuator longitudinal axis
midplane
base element
the central region
end
sliding bearings
oblique section
oblique section
joint
Symmetry plane longitudinal direction N2011 / 03300

权利要求:
Claims (25)
[1]
A bending press (1) comprising a fixed table (3) connected to a machine part (2), a guide assembly (4) on the machine frame (2), with at least one drive means (6) in the direction of and pressing bars (5) adjustable from the table (3), mutually opposite supporting surfaces (9, 10) on the table (3) and on the pressing bar (5) for bending tools (11, 12) and / or insertable tool receiving devices and an adjusting device (20) on the table (3) or on the pressing beam (5) for the active adjustment of a support surface (9) between a substantially planar and a cambered course (19), wherein the support surface (9) of a over the total length (16) of the table ( 3) and / or press beam (5) extending beam element (14) of the table (3) or the press beam (5) is formed, which is supported with a support structure (19) of the table (3) or press beam (5), characterized in that the support structure (1 9) has at least one elongate support element (22) which can assume a helix angle (23) at least in sections with respect to the adjustment direction (21) of the press beam (5), and the control device (20) has a transverse direction to the adjustment direction (21) Support structure (19), in particular the support member (22) acting actuator (24), with which the helix angle (23) of the support member (22) within the table (3) and / or press bar (5) can be changed.
[2]
2. bending press (1) according to claim 1, characterized in that the support structure (19) comprises a plurality of obliquely extending support elements (22).
[3]
3. bending press (1) according to claim 1 or 2, characterized in that the helix angle (23) of the at least one oblique support member (22) within a plane parallel to the adjustment of the press bar (5) plane. N2011 / 03300
[4]
4. bending press (1) according to one of the preceding claims, characterized in that the at least one support element (22) between two to the adjustment plane of the press bar (5) parallel guide plates (43) is guided.
[5]
5. bending press (1) according to claim 4, characterized in that the guide plates (43) at their distance from the beam element (14) end portions (44) by means of a lower chord (45) with each other or with a beam of the element (14) from after Support element (22) arranged base element (27) are fixedly connected.
[6]
6. bending press (1) according to any one of the preceding claims, characterized in that a longitudinal dimension of the at least one support element (22) in its supporting direction at least three times its cross-sectional dimension corresponds to the beam element (14) parallel direction.
[7]
7. bending press (1) according to any one of the preceding claims, characterized in that between the support element (22) and the beam element (14) or between the support element (22) and the fixed part of the support structure (19) in the longitudinal direction of the beam element (14 ) movable sliding bearing (30) is formed.
[8]
8. bending press (1) according to any one of the preceding claims, characterized in that the support elements (22) and the actuators (24) with respect to a longitudinal axis of the beam element (14) perpendicularly extending center plane (26) of the bending press (1) are arranged symmetrically ,
[9]
9. bending press (1) according to any one of the preceding claims, characterized in that a plurality of adjacent support elements (22) formed by in a plate-like base member (27) of the table (3) or the press beam (5) introduced oblique slots (39) are, wherein the slots (39) completely pass through the base member (27). N2011 / 03300 ** - 3Γ-
[10]
10. bending press (1) according to any one of the preceding claims, characterized in that the support structure (19) comprises a plurality of obliquely verlautende support elements (22) with different sized cross-sectional areas.
[11]
11. bending press (1) according to any one of the preceding claims, characterized in that the support structure (19) comprises a plurality of obliquely extending support ele- ments (22) with respect to the adjustment direction (21) different helix angles (23).
[12]
12. bending press (1) according to any one of the preceding claims, characterized in that the helix angle (23) of support members (22) in the central portion (28) of the Balkenefements (14) are greater than those of closer to the end portions (29) arranged support elements (22).
[13]
13. bending press (1) according to any one of the preceding claims, characterized in that the beam element (14) aulweist over its entire length (16) has a substantially constant bending stiffness.
[14]
14. bending press (1) according to any one of the preceding claims, characterized in that the helix angle (23) of the support element (22) or the support elements (22) relative to the adjustment direction (21) is between 0 ° and 45 °.
[15]
15. bending press (1) according to one of the preceding claims, characterized in that adjacent support elements (22) within a portion of the beam element (14) oriented obliquely in the same direction.
[16]
16. bending press (1) according to any one of the preceding claims, characterized in that the support element (22) or the support elements (22) with respect to a Verstelirichtung (21) perpendicular plane of symmetry (34) in the form of a fishbone structure (38) substantially symmetrically two in relation to the adjustment direction (21) of the press beam (5) opposite directions N2011 / 03300 inclined sections

and the force introduction direction of the actuator (24) lies substantially in the plane of symmetry (34) of the support element (22).
[17]
17. Bending press (1) according to one of the preceding claims, characterized in that the support structure (19) comprises a plurality of support elements (22) with oblique support portions (31, 32) formed Stützrauten (40) and the force introduction direction of the actuator (24) in Substantially in the direction of adjustment (21) right-angled plane of symmetry (34) of the Stützrauten (40).
[18]
18. Bending press (1) according to claim 16, characterized in that between adjacent Stützrauten (40) each have their own actuator (24) is provided.
[19]
19. bending press (1) according to any one of the preceding claims, characterized in that at least one of the actuator (24) connected to the inclined support member (22) in the central portion (28) of the beam element (14) is arranged and the support structure (19) to the End portions (29) of the beam member (14) has a higher rigidity in the adjustment direction (21), as the not kraftbeaufschiagte by the actuator inclined support member (22).
[20]
Bending press (1) according to one of the preceding claims, characterized in that at least two oblique support elements (22) connected to an actuator (24) are arranged on the end sections (29) of the beam element (14) and the support structure (19) in Central portion (28) of the beam member (14) has a higher rigidity in the adjustment direction (21), as the not force urged by the actuators oblique support members (22).
[21]
21. Bending press (1) according to one of the preceding claims, characterized in that the at least one support element (22) with at least one end on the beam element (14), on the support structure (19), on the table (3) or on the pressing beam (5). is mounted by means of a hinge (33). N2011 / 03300

[22]
22. Bending press (1) according to one of the preceding claims, characterized in that the at least one support element (22) with at least one end in one piece on the beam element (14), on the support structure (19), on the table (3) or on the pressing beam ( 5) is formed.
[23]
23. Bending press (1) according to one of the preceding claims, characterized in that a support element (22) or a plurality of support elements (22, 22 ', 22 ", ...) with an actuator (24) only indirectly with the interposition of another support member (22) are in communication.
[24]
24. bending press (1) according to any one of the preceding claims, characterized in that between adjacent support elements (22) webs (36) or spacer elements (37) are arranged for mutual power transmission.
[25]
25. bending press (1) according to any one of the preceding claims, characterized in that in the support structure (19) a plurality of transverse to the adjustment (21) acting on the support elements (22) actuators (24) are arranged, which by a controller (42) the bending press (1) are controlled and individually or at least in groups with different adjustment can be activated. TRUMPF Maschinen Austria GmbH & Co. KG. by attorneys Buraer & Partner Attorney GmbH N2011 / 03300

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同族专利:

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引用文献:

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CN113426858B|2021-08-27|2021-11-05|佛山市阿玛达机械科技有限公司|Door leaf bending forming device for fireproof door production and using method thereof|

法律状态:
2018-10-15| MM01| Lapse because of not paying annual fees|Effective date: 20180213 |

优先权:

申请号 | 申请日 | 专利标题

AT1822012A|AT512174B1|2012-02-13|2012-02-13|BENDING COMPRESSION WITH ADJUSTABLE BEAM ELEMENT|AT1822012A| AT512174B1|2012-02-13|2012-02-13|BENDING COMPRESSION WITH ADJUSTABLE BEAM ELEMENT|

PCT/AT2013/050036| WO2013120123A1|2012-02-13|2013-02-12|Bending press with adjustable beam element|

EP13713068.8A| EP2814627B1|2012-02-13|2013-02-12|Bending press with adjustable beam element|

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