EP2512791A2 - Dispositif d'entraînement pour une presse de pliage - Google Patents

Dispositif d'entraînement pour une presse de pliage

Info

Publication number
EP2512791A2
EP2512791A2 EP10807581A EP10807581A EP2512791A2 EP 2512791 A2 EP2512791 A2 EP 2512791A2 EP 10807581 A EP10807581 A EP 10807581A EP 10807581 A EP10807581 A EP 10807581A EP 2512791 A2 EP2512791 A2 EP 2512791A2
Authority
EP
European Patent Office
Prior art keywords
piston
drive device
press
cylinder
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP10807581A
Other languages
German (de)
English (en)
Inventor
Rudolf Scheidl
Peter Ladner
Karl Ladner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Trumpf Maschinen Austria GmbH and Co KG
Original Assignee
Trumpf Maschinen Austria GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Trumpf Maschinen Austria GmbH and Co KG filed Critical Trumpf Maschinen Austria GmbH and Co KG
Publication of EP2512791A2 publication Critical patent/EP2512791A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses

Definitions

  • the invention relates to a drive device, as described in the preamble of claim 1.
  • the linear actuator is formed by a double-acting hydraulic cylinder, wherein a cylinder housing is fixed to the press frame or the adjustable press beam and an adjusting means of a piston assembly is connected to the adjustable press beam or the press frame or the fixed press beam.
  • the hydraulic pump of the drive system is driven by means of a drive motor with rotational direction and speed control.
  • JP 2002 147404 A discloses a hydraulic drive system for a hydraulic cylinder having a plurality of pressure chambers as a closed hydraulic system with a reversibly driven hydraulic pump arranged in a ring line.
  • a pressure accumulator is provided, which is flow-connected via a control valve and a connecting line at least with a wiring harness of the ring line.
  • the object of the invention is to provide a drive device with a hydraulic system for an adjustable press beam of a bending press, with which a high overall efficiency of the drive device is achieved with low energy consumption and low emissions in all operating conditions.
  • This object of the invention is achieved by the reproduced in the characterizing part of claim 1 features.
  • the surprising advantage here is that by forming a bar adjusting device with at least one linear actuator with at least three pressure chambers controlled via the hydraulic system in accordance with the particular requirements of the particular partial cycle of an overall adjusting cycle to be performed, a sensitive adjustment of the required pressure and Volume of pressure medium and thus an optimization and adjustment of the required pump performance as well as the adjustment speed is achieved.
  • this additional control processes for optimizing the adjustment of the adjustable press bar and a total cycle time is achieved.
  • a further advantageous embodiment is also described in claim 9, because an optimization of the pressure medium flow for the different adjustment processes in terms of adjustment speed and power requirement is achieved.
  • Figure 1 shows a drive device according to the invention on a press brake, the example of a drive axle for an adjustable press beam, partially cut.
  • Fig. 2 shows another embodiment of the drive device according to the invention with an advantageous embodiment of the drive axle, partially cut;
  • FIG. 3 shows a further embodiment of the drive device according to the invention with a linear actuator designed as a tandem cylinder, partially cut away;
  • FIG. 4 shows another embodiment of the linear actuator designed as a tandem cylinder, partially cut away; 5 shows a further embodiment of the linear actuator designed as a tandem cylinder, partially cut away;
  • FIG. 6 shows another embodiment of the drive device with the tandem cylinder and a hydraulic system in a first circuit
  • Fig. 8 shows the drive device with the tandem cylinder and a hydraulic system in a third circuit.
  • the drive device 1 shows a simplified representation of a drive device 1 for a relative to a fixed press bar 2 a bending press 3 adjustable press bar 4 is shown.
  • the drive device 1 further comprises a hydraulic system 5 which, in the illustrated and described embodiment, represents a simplified basic version of a beam adjustment device 6 for a hydraulic linear actuator 7. If several of the linear actuators 7 are provided for the adjustment of the press bar 4 in a parallel operation, this must be taken into account with regard to its performance in the technical design of the hydraulic system 5.
  • linear actuators 7 these can be operated both jointly via a hydraulic system 5 or via one, each of the linear actuators 7 associated hydraulic system 5.
  • the (The) hydraulic system (s) is (are) connected to a control and regulating device 8 of the bending press 3 via at least one control line 9 and thus involved in a control and control sequence control.
  • a press station 10 is formed according to the embodiment shown by the attached to side stands 11, fixed press beams 2 and a, various hydraulic, mechanical and electrical equipment receiving cross-dressing 12, and arrives as a compact unit on a footprint 13 for installation.
  • the adjustable press bar 4 as shown, for example, adjustable in linear situationssan- orders 14 on the press frame 10 or the side uprights 11 - according to double arrow 15 - mounted adjustable in the direction perpendicular to the footprint 13 direction.
  • bending tools 18 for the deformation of a workpiece 20 are arranged interchangeably, often in separate tool holders.
  • the bending tools 18 are, in particular, one or more bending punches and one or more bending dies, which are combined according to a planned forming process as needed into a respective set of tools.
  • the linear actuator 7 of the beam adjusting device 6 is mounted according to the embodiment shown with an actuator housing 22 on the press frame 10, for example on a side surface of the side stand 11, and executed in the illustrated embodiment as a stacking cylinder 23.
  • a common adjusting means 24, such as a first piston assembly 25 and a second piston assembly 26 having a first piston 27 and a second piston 28 is drivingly connected to the adjustable press beam, in particular, the adjusting means 24 in a protruding from the actuator housing 22 end portion 29 with the adjustable press bar 4 connected via a spherical bearing assembly 30.
  • the adjusting means 24 forms according to this embodiment, a first piston rod 31 with the first piston 27 and a second piston rod 32 with the second piston 28 wherein the piston rods 31, 32 and thus the piston assemblies 25, 26 are rigidly connected together and the pistons 27, 28th are aligned concentrically with respect to a central axis 33.
  • a first cylinder chamber 34 of the linear actuator 7 is divided by the piston 27 of the first piston assembly 25 in a first pressure chamber 35 with a first piston effective surface 36 and a second pressure chamber 37 with a second piston effective surface 38 pressure-tight.
  • a further cylinder space 39 with the second piston arrangement 26 with the piston 28 forms a one-sided acting cylinder with a pressure chamber 40 and a third piston acting surface 41.
  • the hydraulic effect piston effective surfaces 36, 38, 41 for the adjustment and force application on the adjustable press bar 4 for the different requirements for the respective cycle portion of an entire adjustment cycle of the press bar 4 - as will be discussed later - achieved.
  • the dimensioning of the piston effective surfaces 36, 38, 41 is such that approximately the first piston effective surface 36 of the sum of the second piston effective surface 38 and third piston effective surface 41 corresponds, wherein the press beam 4 adjusting hydraulic direction of action - according to arrow 44 - the first piston assembly 25 with the first piston effective surface 36 is directed in the direction of the fixed press beam 2.
  • the second effective piston area 38 of the first piston arrangement 25 and the effective piston area 41 of the second piston arrangement 26 are decisive for an opposite direction of action.
  • linear actuator 7 with the mechanically rigidly connected piston assemblies 25, 26 thus has the pressure chambers 35, 37, 40 with the associated hydraulically effective piston effective surfaces 36, 38, 41, whose total area annihilates taking into account their hydraulic effective direction.
  • the design as a stacking cylinder 23 causes a very compact linear actuator 7 which is mounted on the press frame 10 in a small footprint via the actuator housing 22.
  • the actuator housing 22 can be embodied both in one-piece construction as well as in a multi-piece design with concentric cylinder chambers 34, 39 centered on one another.
  • the rigid coupling of the second piston assembly 26 with the first piston assembly 25 is effected via a mechanical connection of the piston rod 32 of the second piston assembly 26 with the piston 27 of the first piston assembly 25.
  • the beam adjusting device 6 and shown in FIG 5 is a simplified, reduced to the basic functions version for operating the bending press 3 with the components of a hydraulic pump 46 with drive motor 47 and a control valve 48 and required lines.
  • the hydraulic pump 46 is preferably a hydraulic four-quadrant machine, wherein the main pressure stress mainly in a working stroke - as indicated by arrow 44 - occurs, that is, when immediately a deformation of the workpiece 20 between the bending tools 18 takes place. It is therefore also possible, the hydraulic pump 46 as one-sided acting pump, as it can be operated in the other quadrants at much lower pressures.
  • the drive motor 47 is, for example, a speed-controllable and reversible electric motor and operates in all four quadrants to move the press bar 4 up and down, as indicated by arrows 44, 45.
  • the control valve 48 is used for rapid traverse operation, wherein it is in the switching position shown "0" to the rapid traverse position and the other switching position "1" - which is achieved in electrical control by the control and regulating device 8 - to the working position.
  • the control valve 48 is, for example, an electrically switchable and spring-returnable 2-position valve.
  • the Eilgangsbesclien takes place for a high acceleration and speed and the Ningangsbesclien for low acceleration and speed, the Arthur- bebesclien relates to a Automatverstellweg minimum partial path in the reverse range of the stroke.
  • the piston-active surfaces 36, 41 are designed so that the resulting, hydraulic effective area in this circuit corresponds approximately to that of the piston-active surface 38.
  • the behavior of a synchronous cylinder with an annular surface corresponding to the piston acting surface 38 is modeled. This enables active acceleration in the cycle range - rapid traverse downwards.
  • the ratio of the piston effective surfaces 36, 38 corresponds to the speed ratio between the part cycle rapid traverse movement and working movement at the same pump speed.
  • Piston effective surface 36 is supplied, which is viewed from the hydraulic piston effective surfaces 36, 38, 41 ago behaves the behavior of a Gleichgangzylinders.
  • the subcycle operation movement in the direction of the fixed press bar 2 closes in consequence of the sub-cycle relief movement in the fixed press bar 2 opposite direction, with a controlled decompression of the pressure medium and relief of the press beams 2, 4 and the press frame 10 is achieved and in which a Springback reshaping takes place on the workpiece. Hydraulically, this is done at the reversing the direction of rotation and thus counter-directed promotion of the pressure medium by the hydraulic pump 46 as already described above for operation movement position "1" of the control valve Wiring for the further part cycle rapid traverse movement in direction opposite to the stationary press beam 2 direction, after the decompression movement an angular measurement of the deformation and optionally a post bending process for correcting the bending angle.
  • FIG. 2 shows a further embodiment of the drive device 1 with the hydraulic system 5 for actuating the linear actuator 7 for driving the adjustable press bar 4 of the press brake 1, which may be independent of itself. As already shown, this is illustrated by the example of only one drive axle It is mentioned that in a parallel operation with appropriate design of the hydraulic components and several of the linear actuators 7 are possible and quite common with corresponding higher forming rates.
  • a first control valve 55 and a second control valve 56 is provided for connecting the linear actuator 7, which has the first piston arrangement 25 and the second piston arrangement 26, which in turn form the first pressure chamber 35, the second pressure chamber 37 and the third pressure chamber 40.
  • This has the advantage of a valve optimization, since depending on the operating state in high speed and low in the operation lower volume flows to the linear actuator 7, and the pressure chambers 35, 37, 40 are zuzu meetings.
  • the respective control valve can be optimally adapted to the volume flows with regard to the size. Furthermore, this results in the possibility of correspondingly controlling the control valves 55, 56 to realize different overlaps in the control sequence.
  • a control valve 57 is provided as a safety valve for an emergency stop function via which in a first ring line 58 of the pressure chamber 37 via the hydraulic pump 46 and the control valve 56 to the pressure chamber 35 of the first piston assembly 25 is connected, or via a second Ring line 59 and the control valve 56 and a connecting line 59.1 - as shown in dotted lines - with the pressure chamber 40 of the second piston assembly 26 is connected.
  • FIG. 2 is also a further variant of the arrangement of the emergency stop function causing control valve 57 shown - shown in broken lines - after which it is also possible in a connecting line 59.1 between the pressure chamber 40 of the second piston assembly 26 and the ring line 59th provided.
  • the hydraulic system 5 is extended by a reservoir 60 and two non-return valves 61, 62 which can be triggered by pressurization with the reservoir 60 being connected to pump lines 64 via lines 63 in which the check valves 61, 62 are arranged ,
  • the memory 60 serves to accommodate a small volume of the pressure medium, which on the one hand in the closed system during the pressure build-up in the pressing or for temperature compensation or to compensate for minor leaks is additionally required or must be recorded. Therefore, with appropriate tightness of the system, from which can be expected, the storage volume can be kept extremely low.
  • the pressure in the hydraulic system and thus in the reservoir 60 is low and does not play a significant role in the overall function, but helps prevent cavitation of the hydraulic pump 46 at high accelerations.
  • the memory 60 is functionally an airtight, pre-stressed tank. Via the unlockable check valves 61, 62 pressure medium from the memory 60 in the hydraulic circuit can be switched on or discharged. This is necessary, for example, when pressurizing or disassembling in a larger, hydraulic capacity. Furthermore, when the temperature changes, the required compensating volume is only supplied or discharged by these check valves 61, 62 in the desired operating states.
  • FIG. 3 shows a further embodiment of the linear actuator 7 for driving the adjustable press bar 4.
  • the linear actuator 7 is formed according to this embodiment as a tandem cylinder 65 and optionally has a single or multi-piece cylinder housing 66, with the parallel to each other according to this embodiment cylinder chambers 34, 39 with the double-acting, first piston assembly 25 with the pressure chambers 35, 37 and The single-acting, second piston assembly 26 with the pressure chamber 40.
  • the piston assemblies 25, 26 thus form the three pressure chambers 35, 37, 40 with the associated piston effective surfaces 36, 38, 41, with respect to the effective direction, according to the - arrows 44, 45 - As already shown in FIG. 1, are oriented.
  • the single or multi-piece cylinder housing 66 is fixed to the press frame 10, as simplified.
  • the piston rods 31, 32 of the piston assemblies 25, 26 are in each case drive-connected via the bearing arrangements 30 to the adjustable press beam 4, whereby a rigid coupling of the piston assemblies 25, 26 is achieved via this.
  • FIG. 4 shows a further embodiment of the linear actuator 7 of the drive device 1 for adjusting the press bar 4 of the bending press 3.
  • the linear actuator 7 is also formed according to this embodiment by the tandem cylinder 65 with the single or multi-piece cylinder housing 66 and has the double-acting, first piston assembly 25 and the parallel directed, single-acting second piston assembly 26 with the three pressure chambers 35, 37, 40th and the respectively associated piston effective surfaces 36, 38, 41 with the corresponding area ratio as already described above.
  • the cylinder housing 66 is attached to the press frame 10. According to this embodiment, the rigid coupling of the piston assemblies 25, 26 also takes place via the adjustable press bar 4, wherein the adjusting means 24, or the piston rod 31, the first piston assembly 25, the cylinder housing 66 projects beyond in the direction of the fixed press beam 2 and the bearing assembly 30th is connected to the adjustable press bar 4.
  • the unilaterally acting piston assembly 26 projects beyond the cylinder housing 66 in the opposite direction to the Kolbena- 25 with the piston rod 32, which acts on a cylinder housing 66 partially projecting support arm 67 of the adjustable press bar 4 and is connected to this movement.
  • the coupling of the piston assemblies 25, 26 is achieved via the press beam, whereby they are rigidly coupled with respect to their degrees of freedom of movement.
  • FIG. 5 shows a further embodiment of the linear actuator 7 for driving the adjustable press bar 4 using the example of a drive axle.
  • the linear actuator 7 is formed according to this embodiment as a tandem cylinder 65 and optionally has a single or multi-piece cylinder housing 66, with the parallel to each other according to this embodiment cylinder chambers 34, 39 with the double-acting, first piston assembly 25 with the pressure chambers 35, 37 and the second, after this embodiment also double-acting piston assembly 26, with the pressure chamber 40 and a further pressure chamber 70th
  • the loading of the linear actuator 7 with the pressure medium takes place via the hydraulic system 5 in a configuration adapted to the four pressure chambers 35, 37, 40, 70.
  • the cylinder housing 66 is attached to the press frame 10, according to the embodiment shown on the side stand 11.
  • the piston arrangements 25, 26 with the pistons 27, 28 have continuous piston rods 73, 74 projecting through the actuator housing 66 against opposite end walls 71, 72.
  • the press beam 4 facing end portions 75, 76 of the piston rods 73, 74 are drivingly connected to the press bar 4 via one of the bearing assemblies 30, whereby a non-positive and non-positive connection of the piston assemblies 25, 26 is achieved.
  • the cylinder chambers 34, 39 each have a same inner diameter 77.
  • each of the piston rods 73, 74 of the piston assemblies 25, 26 has, divided by the pistons 27, 28, a first rod portion 78 with a diameter 79 and a second rod portion 80 with a diameter 81 that are different from the dimensions.
  • an activation of the actuator 7 with the closed hydraulic system 7 with the pressure medium can be optimized to the respective requirements with regard to the adjustment speed and force application for the adjustment processes of the individual working cycles, such as - rapid lift down, power stroke down, relief lift up and express lift up - can be achieved.
  • the total volume of pressure medium can be designed to be low, and further reduces the volume to be delivered via the pump in the hydraulic system with the advantage of a smaller one Dimensioning of the valves, the hydraulic pump with drive and the lines.
  • each drive axis of the bending press 2 for the optimization of the motion sequences, with the different requirements of the sub-cycles of an entire adjustment cycle, e.g. Adjustment speed, force application, quite a few linear actuators 7 are quite possible according to the invention and the number of with the
  • Pressure medium of a hydraulic system 5 acted upon pressure chambers 35, 37, 40 may well be more than three.
  • FIGS. 6 to 8 show a further embodiment of the closed hydraulic system 5 of the bar setting device 6 with the hydraulic pump 46 and valves 90, 91, 92, 93, using the example of controlling the linear actuator 7 of a drive axle of the bending press 3.

Landscapes

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

Abstract

L'invention concerne un dispositif d'entraînement (1) pour une presse de pliage (3), notamment une presse à chanfreiner, comprenant un bâti (10) doté d'une poutre (2) fixe et d'une poutre (4) réglable par rapport à la poutre (2) au moyen d'un dispositif de réglage (6) constitué d'un système hydraulique (5) fermé et comportant une pompe hydraulique (46) dotée d'un moteur d'entraînement (47) réglable, au moins d'un clapet de distribution (48) et au moins d'un actionneur linéaire hydraulique (7). L'actionneur linéaire (7) présente un premier ensemble piston (25) doté d'un premier piston (27) subdivisant un espace cylindrique (34) en une première chambre de pression (35) et une deuxième chambre de pression (37), et un deuxième ensemble piston (26) qui est logé dans un autre espace cylindrique (39) et qui est doté d'un autre piston (28), et au moins une autre chambre de pression (40). Le premier ensemble piston (25) et le deuxième ensemble piston (26) sont couplés.
EP10807581A 2009-12-17 2010-12-15 Dispositif d'entraînement pour une presse de pliage Withdrawn EP2512791A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA2004/2009A AT509239B1 (de) 2009-12-17 2009-12-17 Antriebsvorrichtung für eine biegepresse
PCT/AT2010/000482 WO2011079333A2 (fr) 2009-12-17 2010-12-15 Dispositif d'entraînement pour une presse de pliage

Publications (1)

Publication Number Publication Date
EP2512791A2 true EP2512791A2 (fr) 2012-10-24

Family

ID=43983577

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10807581A Withdrawn EP2512791A2 (fr) 2009-12-17 2010-12-15 Dispositif d'entraînement pour une presse de pliage

Country Status (4)

Country Link
US (1) US9688041B2 (fr)
EP (1) EP2512791A2 (fr)
AT (1) AT509239B1 (fr)
WO (1) WO2011079333A2 (fr)

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EP2952750B1 (fr) * 2014-06-04 2018-09-05 MOOG GmbH Système hydraulique
DE102014214739B3 (de) * 2014-07-28 2015-12-31 Trumpf Werkzeugmaschinen Gmbh + Co. Kg Stanzvorrichtung, verfahren zum stanzen eines werkstücks und computerprogrammprodukt zur durchführung des verfahrens
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EP3109488B1 (fr) 2015-06-25 2017-12-13 MOOG GmbH Entraînement hydraulique de fonctionnement sécurisé
DE102016113882A1 (de) * 2016-07-27 2018-02-01 Moog Gmbh Elektro-hydrostatisches Antriebssystem
US11618232B2 (en) * 2017-08-01 2023-04-04 Moog Gmbh Apparatus for controlling the switch-over of hydraulic cylinders
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Also Published As

Publication number Publication date
US20120272708A1 (en) 2012-11-01
AT509239B1 (de) 2013-03-15
US9688041B2 (en) 2017-06-27
WO2011079333A2 (fr) 2011-07-07
WO2011079333A3 (fr) 2011-10-13
AT509239A1 (de) 2011-07-15

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