WO2007090668A1 - Servo-presse - Google Patents

Servo-presse Download PDF

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Publication number
WO2007090668A1
WO2007090668A1 PCT/EP2007/001125 EP2007001125W WO2007090668A1 WO 2007090668 A1 WO2007090668 A1 WO 2007090668A1 EP 2007001125 W EP2007001125 W EP 2007001125W WO 2007090668 A1 WO2007090668 A1 WO 2007090668A1
Authority
WO
WIPO (PCT)
Prior art keywords
press according
drive
plunger
press
axis
Prior art date
Application number
PCT/EP2007/001125
Other languages
German (de)
English (en)
Inventor
Matthias Scheitza
Peter Groche
Original Assignee
Pressenservice Scheitza Gmbh
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 Pressenservice Scheitza Gmbh filed Critical Pressenservice Scheitza Gmbh
Priority to EP07711493A priority Critical patent/EP1984169A1/fr
Publication of WO2007090668A1 publication Critical patent/WO2007090668A1/fr

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
    • B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/10—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism
    • B30B1/14—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism operated by cams, eccentrics, or cranks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/007—Means for maintaining the press table, the press platen or the press ram against tilting or deflection
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/041—Guides
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/14—Control arrangements for mechanically-driven presses

Definitions

  • the invention relates to a press, in particular a servo press for forming and stamping of components.
  • Presses have been known for a long time. With regard to their underlying principle of action, they differ in tied-down, power-bonded and energy-bonded press machines. Essential criteria for the evaluation of presses are the number of strokes (frequency), pressing force, table size (size of the plunger) and accuracy of the plunger movement and the reversal point in the lower end position (UT). It is common to all press types that a ram moving in a plane-parallel manner relative to the press table performs work by applying pressing forces.
  • the torque required for the operation is usually provided by the energy stored in an inertial mass (flywheel) and converted into work on the ram via a crank drive, a spindle or a linkage.
  • a crank drive a crank drive
  • a spindle a linkage
  • JP-A-2003-230996 A a press is described, which has a plurality of drive spindles, which are jointly controlled via a master-slave control. Regardless of the particular load and the resulting deformation of individual drive spindles, the drive spindles are uniformly positioned and held in synchronism. This makes it possible to correct the misalignment (tilting) of the plunger with a possible eccentric load.
  • the slave spindles are controlled in such a way that they exactly follow the movement of a master spindle. If, due to different deformations, a slave spindle lags the master spindle, the controller attempts to return to the position of the master spindle by means of a higher traversing speed of the slave spindle.
  • the selection of the master spindle is fixed by the NC control. However, if - which is already reasonable for economic reasons - the entire press is operated close to its performance limit and one of the slave spindles is moved with their respective maximum permissible power, it is impossible to supply them with even higher power. Such a system can only be safely operated in the range of rated load, if in addition to the position of each individual spindle and their current load is detected and based on this measurement, the highest loaded spindle is selected as the master spindle.
  • the invention has for its object to provide a press, are reliably compensated in the misalignment of the plunger by off-center force application via the drive to ensure a perfect plane-parallel operation of the plunger, the plunger but also, to implement new forming process, intentional tilting or can perform wobbling movements with high energy economy and high stroke rates.
  • the object is achieved by a press, with a press frame, a plunger device and at least two drive devices which act together on the plunger device and cause a movement of the plunger device, each of the drive devices has its own drive and a controller is provided with the Drive devices are individually and independently controlled.
  • the plunger device can be movable relative to the press frame with at least two degrees of freedom, namely with a vertical movement in the direction of the vertical axis (z-axis) and with a tilting movement about a first horizontal axis (x-axis).
  • the plunger device can be moved relative to the press position with at least two degrees of freedom, a tilting or tumbling movement about the first horizontal axis can be realized in addition to the translational, plan-parallel main forming movement which the plunger device must perform during operation.
  • the plunger means may be movable relative to the press frame even with three degrees of freedom, namely with said vertical movement in the direction of the vertical axis (z-axis), with the tilting movement about the first horizontal axis (x-axis) and additionally with a Tilting movement about a second horizontal axis (y-axis).
  • the vertical movement represents the main forming movement that the plunger device has to perform during operation.
  • the plunger device can also be pivoted or tilted relative to the horizontal plane, specifically around the first and optionally around the second horizontal axis, by the individual actuation of the drive devices and by the provision of the corresponding degrees of freedom.
  • the plunger device can also be pivoted or tilted relative to the horizontal plane, specifically around the first and optionally around the second horizontal axis, by the individual actuation of the drive devices and by the provision of the corresponding degrees of freedom.
  • the tilting position of the plunger device can already be set before the plunger device comes into contact with the component to be formed, that is, still experiences no pressing force. However, it can also be set or changed during the work process.
  • each drive device can be controlled individually for itself, without having to take into account the movement of the other drive devices.
  • a feedback takes place only via the movement of the plunger device.
  • suitable trajectories can also be recorded and stored for the respective forming process, which are subsequently traversed in continuous operation.
  • the individual controllability of the drives of the drive devices makes it possible for the drives to precisely comply with the respective trajectories stored for them, so that the plunger device also follows the desired movement.
  • the drive devices can be designed as revolving crank drives, wherein the circulation is to be maintained even with a stroke smaller than the maximum stroke. It is therefore necessary to supplement the press with a device for stroke adjustment. It has been found that known arrangements for stroke adjustment z. B. could be disadvantageous by eccentric, since each eccentric device must be upgraded with a separate device for changing the effective radius in order to adjust the lift height can.
  • each eccentric is equipped with a separate, position-monitored adjusting drive, or inaccurate, provided that the adjustment of the eccentric via a central drive, its movement via shafts (torsion elastic) and bevel gear (game) to the individual Antriebsvorichtun- must be diverted.
  • crankpin device As coupled with the drive crank connecting rod device not only crank mechanisms, but also eccentric drives are to be understood with a central stroke adjustment. For simplicity, only the term crankpin device is used for this purpose.
  • each of the drive devices comprises an at least six-link linkage or toggle linkage coupling the drive with the ram device, which has a crank-connecting device coupled to the drive and further gear elements and joints.
  • the linkage has a crank lever device downstream of the crank connecting rod device.
  • the linkage can have a lifting height adjustment device with which a lifting height of the ram device is adjustable. It is state of the art that the lifting height can be set exactly to hundredths of a millimeter in presses. This possibility is accordingly also in the press according to the invention feasible.
  • the linkage can have a mounting height adjustment, with which the installation height of the plunger device can be adjusted. This makes it possible to adapt the height position of the plunger device to the workpiece to be machined, in particular to its thickness or to the tool to be inserted between the plunger and the table.
  • the lifting height adjusting device and / or the installation height adjusting device can be arranged such that they are not or only partially loaded by a force acting perpendicular to the plunger device pressing force.
  • the pressing force is naturally very high, so that there is a danger that the lifting height or the installation height adjustment could be damaged if the pressing force would be completely discharged through them. By appropriate arrangement can prevent this.
  • the lifting height adjusting device may have a spindle device with which the lifting height can be adjusted in a very simple, but reliable and robust manner.
  • the lifting height adjusting devices of all the drive devices have a common central adjustment device. With the help of the central adjustment can then uniformly adjust the lifting height of all drive devices. This not only facilitates the operation of the press, but also reduces the mechanical structure, since then no longer every single Hubtownn- Adjustment, for reasons of required accuracy to each other, must be fully equipped for individual adjustment.
  • the common central adjusting device can have a common spindle device.
  • three drive devices are provided, which are arranged in a star shape on the plunger device.
  • the three drive devices thus form a tripod, which can absorb forces reliably.
  • the plunger device can be guided via a guide device on a press frame. In this way it is ensured that the plunger device has a solid mechanical guide to absorb shear forces.
  • the tilting movement can also be performed during the forming process, which allows certain forming operations.
  • a wobbling movement of the plunger device can be generated by a coordination or superimposition of the tilting movements.
  • the guiding device may comprise three vertical guides and three decoupling devices arranged between the vertical guides and the ram device, such that the ram device is movable relative to the vertical guides with three degrees of freedom.
  • the plunger device can be moved in this way relative to the press frame with three degrees of freedom, as proposed above.
  • the drive can be realized by a high-torque electric motor. Particularly suitable for this purpose are torque motors that achieve high torque at low speeds.
  • the torque motors are easy to control, which is expedient for the individual control of the drive devices.
  • the drive can also be realized by a hydraulic motor.
  • the linear drive can, for. B have a hydraulic cylinder or a rotationally driven spindle drive.
  • the linear actuator must be provided with a corresponding control that allows precise control of the reversal points or the path-time behavior. Also in this way, the plunger device can be moved in the manner according to the invention relative to the press frame.
  • FIG. 1 shows a schematic representation of a first embodiment of a press according to the invention
  • FIG. 2 shows a second embodiment of the invention with a toggle lever drive.
  • FIG. 3 shows a third embodiment of the invention with a modified lifting and installation height adjusting device
  • Fig. 4 shows a fourth embodiment of the invention with an extended
  • FIG. 5 shows a fifth embodiment of the invention with two symmetrical drive devices.
  • FIG. 7 is a schematic representation of a plan view of a plunger device
  • Fig. 8 is a schematic representation of a guide device for the
  • FIG. 10 is a schematic representation of a drive control
  • FIG. 11 shows a signal flow diagram of the control parameterization from a controller.
  • a press according to the invention has in its simplest design at least two drive devices, which are each equipped with its own drive. With the aid of a controller, the drives can be individually and independently controlled. Each of the drives is connected to a linkage, which has a coupled with the drive crank connecting rod device and other gear members and joints. The linkage couples the drive with a plunger device to which a press tool can be attached.
  • Fig. 1 shows a schematic representation of a six-link transmission or articulated lever transmission with a crank mechanism and three degrees of freedom.
  • the gear elements are marked with n and numbered, the joints corresponding to g.
  • the gear member n4 represents a crank of a crank mechanism.
  • N3 is a connecting rod which acts on a plunger n2.
  • the plunger n2 can be raised and lowered in a guide nl at least in the vertical direction.
  • an eccentric can be used instead of a crank and a crank mechanism also - as stated above - an eccentric can be used.
  • An unillustrated drive in particular an electric motor designed as a torque motor, is arranged in the region of a joint g4.
  • the joint g4 should thus symbolize a drive.
  • the stroke of the ram n2 can be adjusted.
  • the minimum possible stroke is twice the length of the crank n4.
  • a change in the installation height can be done by moving the entire system, in particular also the gear member n6. It has no effect on the set lift height. When changing the stroke, however, the installation height must be readjusted as with an eccentric press.
  • Fig. 2 shows a second embodiment of the invention, a further development of the press.
  • an eight-member linkage (8 gear members, 9 joints) is proposed, in which in addition to the structure of Fig. 1, a toggle lever drive is realized.
  • the drive is now symbolized by the joint g9 and drives a crank n8. Their movement is transmitted to the joint combination g3 / g7 via a joint g8 and a push rod n7.
  • the large-volume drive is now arranged spatially separated from the lifting and installation height adjustment, which still lie together. Likewise, thereby the minimum possible stroke of the unit compared to FIG. 1 can be reduced.
  • Fig. 3 shows a third embodiment of the invention with a toggle lever drive with modified lifting and installation height adjustment.
  • a reduction in the distance between the gear element n9 and the gear element n10 causes a displacement of the joints g4 and g5 coupling the gear elements n5 and n6 and thus an increase in the distance e and a change in the lifting height corresponding to the dependency described above.
  • the tool installation height can be adjusted or the position change of the gear member n2 (plunger) can be compensated by the adjustment process.
  • the gear members n9 and nl O in cooperation with the gear members n5 and n6 and the associated joints together form the Hubtownn- and the installation height adjustment. Since both adjustment movements now take place in the same axis, the structural design is significantly simplified. It is advisable to connect the gear members n9 and n lO via a spindle whose drive z. B. via a splined shaft by a fixed in a press frame not shown motor. The position change of gear member nl O can be introduced via another, frame-fixed spindle to adjust the installation height.
  • Fig. 4 shows a fourth embodiment of a further development of the invention.
  • Fig. 5 shows a further development as a fifth embodiment of the invention, in which two symmetrical drive trains (drive devices) are combined.
  • an adjusting motor 10 which drives a splined shaft and a spindle 12.
  • an adjusting motor 1 1 is provided for changing the installation height, which rotates a spindle 13.
  • FIG. 5 also shows the guide 1, the plunger 2, the connecting rods 3 and the cranks 4, which correspond to the reference numbers of FIG. 1, but without the letter "n".
  • FIG. 6 shows a three-dimensional representation of a star-shaped arrangement of three drive devices, which are arranged around a common spindle for the lifting height adjustment device and the installation height adjustment device.
  • Fig. 7 shows a schematic plan view of a plunger 20 which is held by three vertical guides 21 in a press frame 22.
  • the three degrees of freedom are intended to allow the plunger 20 to be moved in the vertical direction (z-axis) and tilted about the x, the y-axis or any axis in the x-y plane.
  • decoupling devices 23 are provided.
  • Fig. 8 shows the schematic structure of an example of such a decoupling device 23, which allows the desired degrees of freedom due to the provided joints and coupling members.
  • decoupling devices 23 must also be provided in the manner suggested in FIG. 8.
  • Fig. 9 shows a schematic 3D representation of a possible embodiment of the plunger guide, wherein a shown in Fig. 8 pivot 23a is designed as a spherical bearing to compensate for misalignment of the guides to each other. Furthermore, a guide system sits on a guided by two columns 24 bridge 25 to keep access to the tool installation space between the plunger 20 and a table 22 a accessible from all sides.
  • FIG. 10 shows a schematic representation of a drive control for the plunger 20.
  • the setpoint values in the control are the position of the tappet center of gravity q s So "and the tilt angles ⁇ Sx SoI i and ⁇ Sy So ii. So the angular deviations around the center of gravity, given. However, it does not seem absolutely necessary to move the plunger position-controlled in all Beriebsart.
  • Any changes in conditions that may occur during production, eg. B. increase in material thickness, etc., can be detected by a process monitoring, which uses the already existing for the determination of the ram center of gravity and the tilt angle sensors.
  • Fig. 11 shows this control control strategy for clarity graphically as a signal flow diagram.
  • any desired ram forces can be set below a maximum ram force predetermined by the mechanical structure of the press and the torque motor.
  • the tool speed as well as the path-time characteristic of the tool movement is arbitrarily adjustable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)

Abstract

L'invention concerne une presse présentant un dispositif à piston (2, 20) et au moins deux dispositifs d'entraînement qui agissent conjointement sur le dispositif à piston (2, 20) en engendrant un déplacement du dispositif piston (2, 20). Chaque dispositif d'entraînement est équipé de son propre mécanisme d'entraînement (g4; g9). Un dispositif de commande permet de commander les mécanismes d'entraînement (g4; g9) des dispositifs d'entraînement individuellement et indépendamment les uns des autres. Les dispositifs d'entraînement sont couplés à l'aide de la seule commande à l'exclusion de tout autre élément de couplage. Le dispositif à piston (2, 20) peut se déplacer par rapport à un bâti de presse avec au moins deux, notamment trois degrés de liberté, correspondant à un déplacement vertical en direction de l'axe vertical (axe z), à un basculement autour d'un premier axe horizontal (axe y) et à un basculement autour d'un deuxième axe horizontal (axe y).
PCT/EP2007/001125 2006-02-10 2007-02-09 Servo-presse WO2007090668A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07711493A EP1984169A1 (fr) 2006-02-10 2007-02-09 Servo-presse

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006006312A DE102006006312A1 (de) 2006-02-10 2006-02-10 Servo-Presse
DE102006006312.0 2006-02-10

Publications (1)

Publication Number Publication Date
WO2007090668A1 true WO2007090668A1 (fr) 2007-08-16

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ID=37946176

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/001125 WO2007090668A1 (fr) 2006-02-10 2007-02-09 Servo-presse

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EP (1) EP1984169A1 (fr)
DE (1) DE102006006312A1 (fr)
WO (1) WO2007090668A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109435305A (zh) * 2018-12-13 2019-03-08 常州纺织服装职业技术学院 一种高速冲床主传动机构
CN110280633A (zh) * 2019-07-22 2019-09-27 南京邮电大学 具有多工作模式的高速重载全电伺服数控折弯机
CN117048111A (zh) * 2023-06-30 2023-11-14 浙江帅锋精密机械制造有限公司 一种行程可调的多连杆冲床

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102173076A (zh) * 2010-12-14 2011-09-07 山东科技大学 复合驱动机械式伺服压力机
EP2479022A1 (fr) * 2011-01-24 2012-07-25 Osterwalder AG Presse à poudre
DE102016107594A1 (de) * 2016-04-25 2017-10-26 Georg Maschinentechnik GmbH & Co. KG Spielfreier Zwischenantrieb einer Presse mit Servomotor
DE102016012803B4 (de) * 2016-10-26 2019-05-16 Horst Baltschun Presse mit gesteuerter, stabiler Stößelführung
CN110280632B (zh) * 2019-07-22 2024-03-26 南京邮电大学 基于复合驱动的高速重载机械式全电伺服数控折弯机

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2048344A5 (en) * 1969-12-31 1971-03-19 Sp Konstruktors Hydraulic press for stamping of curved - steel sheet
US4318325A (en) * 1979-08-24 1982-03-09 L. Schuler Pressen Gmbh Press drive arrangement
DE19521050A1 (de) * 1994-06-14 1995-12-21 Murata Machinery Ltd Kniehebel-Antriebsvorrichtung
DE10029350A1 (de) * 1999-06-18 2001-01-11 Kyoei Kogyo Co Presseneinheit
US20010002566A1 (en) * 1998-04-30 2001-06-07 Oskar Eigenmann Punch press, specifically a high-speed punch press
US20010039888A1 (en) * 2000-05-11 2001-11-15 Shozo Imanishi Slide drive device for a press
EP1177887A2 (fr) * 2000-08-04 2002-02-06 Matsushita Electric Industrial Co., Ltd. Dispositif de précision pour machine de moulage et méthode d'utilisation
US20020071884A1 (en) * 1999-04-06 2002-06-13 Aida Engineering Co., Ltd Slide guide device, knockout device, and press machine using the same
US20050189900A1 (en) * 2004-02-26 2005-09-01 Joachim Beyer Mechanical press

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2048344A5 (en) * 1969-12-31 1971-03-19 Sp Konstruktors Hydraulic press for stamping of curved - steel sheet
US4318325A (en) * 1979-08-24 1982-03-09 L. Schuler Pressen Gmbh Press drive arrangement
DE19521050A1 (de) * 1994-06-14 1995-12-21 Murata Machinery Ltd Kniehebel-Antriebsvorrichtung
US20010002566A1 (en) * 1998-04-30 2001-06-07 Oskar Eigenmann Punch press, specifically a high-speed punch press
US20020071884A1 (en) * 1999-04-06 2002-06-13 Aida Engineering Co., Ltd Slide guide device, knockout device, and press machine using the same
DE10029350A1 (de) * 1999-06-18 2001-01-11 Kyoei Kogyo Co Presseneinheit
US20010039888A1 (en) * 2000-05-11 2001-11-15 Shozo Imanishi Slide drive device for a press
EP1177887A2 (fr) * 2000-08-04 2002-02-06 Matsushita Electric Industrial Co., Ltd. Dispositif de précision pour machine de moulage et méthode d'utilisation
US20050189900A1 (en) * 2004-02-26 2005-09-01 Joachim Beyer Mechanical press

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109435305A (zh) * 2018-12-13 2019-03-08 常州纺织服装职业技术学院 一种高速冲床主传动机构
CN109435305B (zh) * 2018-12-13 2024-05-07 常州纺织服装职业技术学院 一种高速冲床主传动机构
CN110280633A (zh) * 2019-07-22 2019-09-27 南京邮电大学 具有多工作模式的高速重载全电伺服数控折弯机
CN117048111A (zh) * 2023-06-30 2023-11-14 浙江帅锋精密机械制造有限公司 一种行程可调的多连杆冲床
CN117048111B (zh) * 2023-06-30 2024-04-30 浙江帅锋精密机械制造有限公司 一种行程可调的多连杆冲床

Also Published As

Publication number Publication date
DE102006006312A1 (de) 2007-08-16
EP1984169A1 (fr) 2008-10-29

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