Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
  • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
  • B21D5/0272—Deflection compensating means

Definitions

• the invention relates to a bending press as described in the preamble of claim 1.
• WO 01/43896 A1 discloses a press brake for producing bent-formed workpieces, comprising a table beam fixedly arranged on a machine frame, a pressing beam adjustable relative to it by means of a drive mechanism and guide arrangements on the machine frame and on mutually opposite support surfaces of the table beam and of 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.
• 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 for upward by a corresponding deflection of the ends of the table beam down.
• 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 pressing beam is formed in two parts, wherein a first beam part with the drive means drive s is connected and a table beam facing, further beam part in the region of a central axis via a flexible connecting element with the first beam part drive s is connected. Starting from this connecting element run between the first beam part and the second beam part in the direction of the opposite end portions of conically widening slots.
• the slots are provided with wedge-shaped extensions in which distance elements are arranged 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.
• 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.
• the tool holder which can be fitted with bending tools is supported on the profile.
• a crowning of the contact surface of the tool holder is achieved in order to compensate for bending deformation of the table beam occurring under load.
• a coordinated displacement movement of the wedges is achieved via a, acted upon by a control drive, extending over the entire length of the press brake, elastic spring element, whereby a support surface for the tools or a receiving device for the tools occupies a tailored to the requirements curvature and thus a compensation for the bending of the table beam and / or press beam is achieved over an entire bending length and so the immersion depth of the bending tools over the entire bending length is approximately equal.
• 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 with structurally simple execution form is actively changeable in its course.
• the object of the invention is achieved by a generic bending press with the characterizing features of claim 1.
• the support structure has at least one elongate support member which can take at least partially a helix angle with respect to the adjustment direction of the press beam
• the actuating device comprises a transversely to the adjustment on the support structure, in particular the support member acting actuator, with the helix angle of the support member 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 starting from an initially absent oblique position 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.
• the oblique portions of the support member cause a stronger elastic mobility and it can be relatively easily adjusted by means of the actuators, the inclination and thus the camber sutz 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.
• actuators here are systems that correspond to the drive means of the press beam so for example hydraulic cylinders or servomotors with adjusting spindles.
• 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. It is thus possible, for example, for the expected maximum forming force to be calculated in advance, and for the required curvature of the support surface, and thus also the desired curvature, to be determined on the basis of a dependency between forming force and press beam deflection determined in test series.
• Required angle adjustment of the support element is made before reaching the maximum forming force or even before the start of the forming.
• suitable sensors such as strain gauges or on the detection of the current forming force, for example via the hydraulic pressure or the drive current of the drive means, which is measured in a forming process currently occurring deflection of the press beam or calculated and the press table by Adjustment of the support element during the forming process a curvature of the support surface corresponding to the respective current value of the deflection is actively set.
• 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 causing too strong spring back of a support member the actuator force is counteracted.
• the actuator preferably has a holding function with which, for example, a retraction of a hydraulic piston can be blocked or a parking brake. Furthermore, it is possible that the actuator counteracts by means of a position control and a controlled increase in the actuating forces of an unwanted deformation of the support structure.
• the respective deformation state of the press beam preferably also the support structure by means of suitable sensors, such as Dehnmess strips are determined and based on the corresponding activation of the actuators.
• the beam element can be actively changed at a plurality of support points and the progression curve of the support surface can be made 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.
• 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 In this case, suitable for a pre-calculated or measured during the forming process directly or indirectly measured deflection of the press bar can be produced.
• 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.
• 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 structurally simpler with an elongated beam element and the depth of the press table or beam is not substantially 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.
• 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.
• the guide plates or aprons may be connected to each other at their distant from the beam element edges by means of a lower chord or with a nem of the beam element arranged after the support element arranged base element to be fixed, which as well as a lower flange, the rigidity of the beam element can further increase , which avoids local deformations due to punk-like stress during bending operations. 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 support direction corresponds to at least three times its cross-sectional dimension in the direction parallel to the beam element.
• a displacement bearing movable in the longitudinal direction of the beam element is formed between the support element and the beam element or between the support element and the base element which forms the stationary part of the support structure.
• the second variant is provided if the actuator engages the distanced from the beam element end of the support element.
• An easily manufactured and particularly stable embodiment of a support structure can be produced when a plurality of adjacent support elements are formed by introduced into a plate-like base member of the table or the press beam inclined slots, wherein 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 comprises different helix angles.
• a locally stronger displacement of the beam element with the same displacement path of the actuator can be achieved by a support element arranged in this zone with a larger helix angle.
• Support elements with smaller cross-sectional areas have a higher elasticity and can sol- be provided where a greater compliance of the beam element is desired.
• the shaping drive means engage the end sections of the press beam
• 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 a pressing beam, the crowning or raising the profile curve of the support surface in the middle is most required and this can be achieved by the centrally larger helix angle, even if all the support elements of the same horizontal displacement is impressed.
• 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 if the helix angle of the support element or of the support elements is between 0 ° and 45 ° relative to the adjustment direction, whereby the effect according to the invention can be realized with a support element oriented in the adjustment direction, that is brought 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 takes place 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.
• 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.
• 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.
• this simple construction the harmful deflection of the press beam can be largely compensated.
• An embodiment also with a low number of support elements can 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 middle section of the Beam element has a higher rigidity in the adjustment direction, as the non-force actuated by the actuators oblique support elements.
• the at least one support member is mounted with at least one end on the beam element, the support structure, the table or the pressing beam by means of a hinge or bearing.
• Swivel or plain bearings are used.
• 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 the beam element, on the support structure, on 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 be effected by webs or support elements arranged between adjacent support elements for the mutual transmission of force.
• 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.
• FIG. 1 shows in a highly schematically simplified representation: 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;
• FIG. 2 shows a view of a press table with a possible embodiment of a setting device and supporting structure
• FIG. 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;
• FIG. 5 shows a section of a further possible embodiment of a support structure with supporting elements in the form of a herringbone structure
• FIG. 6 shows a view of a further possible embodiment of an adjusting device and supporting structure with diamond-shaped support elements
• FIG. 7 shows a section through a press table with an adjusting device and a support structure shown in FIG. 6;
• 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
• FIG. 9 is a view of another possible embodiment of an adjusting device and support structure with angled support elements in herringbone structure.
• 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 common embodiment, two spaced-apart side cheeks 7, for example in the form of C-stands, which are connected by means of transverse connectors 8.
• mutually opposite 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.
• 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 and the press beam 5, whereby the bending tools 11, 12 can be selected and positioned according to the requirement of the workpieces 13 to be bent. As shown in Fig.
• 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 ,
• 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.
• the bending press 1 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 angle 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 21 of the press beam 5 and in the adjustment plane, which corresponds to the plane of the drawing in FIG.
• the lower beam element 14 In order to produce such a cambered profile 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 forming 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.
• 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.
• 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.
• a reduction in the helix angle 23 causes the beam element 14 to lift, causing the cambered profile 18 to be effected.
• oblique support element 22 is shown, which simplifies how a point load acts on the beam element 14 from below;
• 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 member 22 is at least slightly displaceable by its elongated design within the support structure 19 and the elongated embodiment is to be understood such that a longitudinal dimension of the support member 22 is greater than its dimension transverse to its longitudinal axis and in the direction of its slight displacement.
• 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 are considered in the illustrated embodiment in comparison to the support member 22 as rigid and immovable can. 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 designed as separate components in the illustrated embodiment, but may also be an integrally connected with the table 3 or pressing bar 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.
• a relatively large 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 motion ratio is achieved, that is, a small displacement on the actuator 24 causes a relatively large, vertical displacement for the bias of the beam element 14.
• the deflection 17 of the beam member 15 in a forming process is in many cases in Substantially symmetrical with respect to a plane perpendicular to the longitudinal axis of the beam member 14 center plane 26 of the bending press 1 fail and it is therefore advantageous if the adjusting device 20 with the oblique support members 22 is designed so that the cambered course 18 of the lower beam member 14 is also symmetrical to Middle plane 26 is effected.
• a very simplified embodiment of a support structure 19 is shown with an inclined support member 22, and are shown in sequence different embodiments of support structures 19, with which using a transverse to the adjustment 21 of the press beam acting on the support structure 19 actuator 24 a cambered profile 18 of a beam element 14 can be achieved.
• 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 dddischen an opposite, active deformation of the beam element 15 to balance. Accordingly, the above and following embodiments are also to be interpreted for embodiments sformen of bending presses 1, in which such oblique support members 22 are provided only on 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 lein plate-like base member 27, such as those are also used in known from the prior art bending presses 1 both for the press table and for the pressing beam.
• support structures 19 there are also columnar embodiments of support structures 19 conceivable, which also include oblique support members 22 and acting on actuators 24.
• An important effect of an oblique support element 22 is the comparatively great mobility in the adjustment direction 21, which is greater than in the case of support elements which are arranged parallel to the adjustment direction 21. This mobility is used in conjunction with the actuator 24 to bias a beam member 14 accordingly.
• 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 middle region.
• 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.
• a sloping support member 22 is arranged, which can be changed by means of an actuator 24 in its skew angle 23.
• the end sections 29 of the beam element 14 or 15 are supported by a part of the support structure 19, which have a higher rigidity in the adjustment direction 21 at the end sections 29 than the inclined support element 22.
• the inclined support element 22 arranged in the middle region 28 can, as already described above, also be replaced by a plurality of such oblique Stützelemen- te 22, 22 ', ....
• 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.
• FIG. 3 is a partial view of another embodiment of a support structure 19 for a
• Beam element 14 of a bending press 1 shown.
• 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 has a higher rigidity in the adjustment direction 21, as the inclined support members 22.
• the two support members 22 can be adjusted by actuators 24 in their position 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 member 14 can be actively adjusted.
• the support elements 22 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 thereby the beam element 14, 15 is adjusted.
• the variant shown in FIG. 3 could also be modified in such a way that the support elements 22 are displaceably mounted at their lower end relative to the base element 27 by means of displacement bearings 30 and the actuators for lowering the lateral ends of the beam element 14, 15 at the lower end of the Assume supporting elements 22 and can exert pressure forces in the direction of the vertical center plane.
• 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 tuator, whereby also the course of the support surface 9, 10 active can be changed.
• FIG. 4 shows a detailed detail of a further embodiment of a support structure 19 with which a beam element 14 can be adjusted under the action of an actuator 24 between a flat and a convexly or concavely curved course, by a support element 22 which faces the beam element 14 the rest of the support structure 19 that is the base member 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.
• 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.
• 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.
• joints 33 on the base member 27 and the beam member 14.
• 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 no separate joints 33 are provided or these are arranged only at certain points of the support element 22.
• 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.
• 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.
• the trajectory 18 of the support surface 9 by the use of multiple support elements 22 is more uniform.
• FIG. 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 in each case two inclined sections 31 and 32, the with respect to the adjustment direction 21 opposing helix angle 23 and with respect to a plane parallel to the longitudinal direction 35 symmetry plane 34 are arranged and executed substantially symmetrically.
• Adjacent support elements 22 in this case have an orientation in the same direction, ie corresponding inclined sections 31 and 32 adjacent support members 22 have in the same direction oriented helix angle 23.
• These helix angle 23 adjacent support members 22 may be identical, but it is also possible that the helix angle 23 of a support element 22 and the support sections 31 and 32 increases and decreases to the adjacent support element or the adjacent support sections 31 and 32.
• 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.
• 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 individual support elements 22 may be embodied as separate components which connect the beam element 14 to the base element 27, but the embodiment shown in FIG. 5 in which the herringbone structure 38 is integrally connected is also advantageous Support elements 22 is formed, which is used as a single contiguous component between the base member 27 and beam member 14 or as shown also integrally connected to the base member 27.
• 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
• 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.
• 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 can be adjusted and thus the curvature of the beam element 14 can be influenced.
• the two outer support rods 40 were supported by further actuators 24 relative to the base element 27 of the table 3.
• 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 beam element 14 parallel
• the upper and lower connection points of the support members 22 are not displaced in the horizontal direction and therefore arise in the horizontal direction and no significant forces between the support member and base member 27 and cross connector 41.
• the cross connector 41 as already described with reference to FIG. 5, also the beam element 14 'form.
• actuators 24 preferably hydraulic cylinders are used which represent an optimal solution for the low adjustment path required and high adjustment forces.
• spindle drives In support structures in which larger adjustment 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 simultaneously adjusted by a spindle drive, since it would not be economical for each support member 22 to provide its own spindle drive.
• 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 effected by a control 42 shown in FIG. 1, which, inter alia, can also take into account measured values of the deflection of the press beam 5 as well as measured values of the active deformation of the beam element 14 and based on control of the profile 18 of the support surface 9 on measured values of the deflection of the Pressbar 5 can generate.
• 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 element 14, so that no local deformations of the beam element occur at punctiform 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.
• 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 oblique angle have 23.
• the upper ends of the oblique support members 22 of a half are combined by means of 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.
• a displacement bearing 30 is provided between the transverse connector 41 and the underside of the beam element 14, whereby no or no appreciable horizontal forces are transmitted between the transverse connectors 41 and the beam element 14.
• the sliding support 30 is preferred 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.
• lateral actuators 24 which are arranged in the region of the plane of symmetry 34 of the herringbone structures 38.
• the herringbone structures 38 according to FIG. 9 essentially correspond to those of the embodiments of FIG. 5 or 6.

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

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• 2012
  • 2012-02-13 AT AT1822012A patent/AT512174B1/de not_active IP Right Cessation
• 2013
  • 2013-02-12 EP EP13713068.8A patent/EP2814627B1/fr not_active Not-in-force
  • 2013-02-12 WO PCT/AT2013/050036 patent/WO2013120123A1/fr not_active Ceased

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