EP0300000B1 - Entrainement pour presse - Google Patents

Entrainement pour presse Download PDF

Info

Publication number
EP0300000B1
EP0300000B1 EP88901014A EP88901014A EP0300000B1 EP 0300000 B1 EP0300000 B1 EP 0300000B1 EP 88901014 A EP88901014 A EP 88901014A EP 88901014 A EP88901014 A EP 88901014A EP 0300000 B1 EP0300000 B1 EP 0300000B1
Authority
EP
European Patent Office
Prior art keywords
drive
energy
toggle levers
toggle
motor
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.)
Expired - Lifetime
Application number
EP88901014A
Other languages
German (de)
English (en)
Other versions
EP0300000A1 (fr
Inventor
Waldemar Hellwig
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.)
Bruderer AG
Original Assignee
Bruderer AG
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 Bruderer AG filed Critical Bruderer AG
Priority to AT88901014T priority Critical patent/ATE65052T1/de
Publication of EP0300000A1 publication Critical patent/EP0300000A1/fr
Application granted granted Critical
Publication of EP0300000B1 publication Critical patent/EP0300000B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • G—PHYSICS
    • G03—PHOTOGRAPHY; CINEMATOGRAPHY; ANALOGOUS TECHNIQUES USING WAVES OTHER THAN OPTICAL WAVES; ELECTROGRAPHY; HOLOGRAPHY
    • G03C—PHOTOSENSITIVE MATERIALS FOR PHOTOGRAPHIC PURPOSES; PHOTOGRAPHIC PROCESSES, e.g. CINE, X-RAY, COLOUR, STEREO-PHOTOGRAPHIC PROCESSES; AUXILIARY PROCESSES IN PHOTOGRAPHY
    • G03C7/00—Multicolour photographic processes or agents therefor; Regeneration of such processing agents; Photosensitive materials for multicolour processes
    • G03C7/26—Silver halide emulsions for subtractive colour processes
    • 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
    • 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
    • B30B1/16—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 fluid-pressure means
    • 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
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0064—Counterbalancing means for movable press elements
    • G—PHYSICS
    • G03—PHOTOGRAPHY; CINEMATOGRAPHY; ANALOGOUS TECHNIQUES USING WAVES OTHER THAN OPTICAL WAVES; ELECTROGRAPHY; HOLOGRAPHY
    • G03C—PHOTOSENSITIVE MATERIALS FOR PHOTOGRAPHIC PURPOSES; PHOTOGRAPHIC PROCESSES, e.g. CINE, X-RAY, COLOUR, STEREO-PHOTOGRAPHIC PROCESSES; AUXILIARY PROCESSES IN PHOTOGRAPHY
    • G03C1/00—Photosensitive materials
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8821—With simple rectilinear reciprocating motion only
    • Y10T83/8841—Tool driver movable relative to tool support
    • Y10T83/8845—Toggle links, one link pivoted to tool support

Definitions

  • the invention relates to a press drive, e.g. for deep-drawing, trimming or punching presses and in particular for high-frequency punching presses with at least 500 punching movements per minute (which, as is known, must be specially designed for this), according to the preamble of claim 1.
  • a press drive e.g. for deep-drawing, trimming or punching presses and in particular for high-frequency punching presses with at least 500 punching movements per minute (which, as is known, must be specially designed for this), according to the preamble of claim 1.
  • a press drive e.g. for deep-drawing, trimming or punching presses and in particular for high-frequency punching presses with at least 500 punching movements per minute (which, as is known, must be specially designed for this), according to the preamble of claim 1.
  • the upper one is movable, but ultimately only the relative movement is important, which is why it would also be conceivable within the scope of the invention to make both tool carriers movable.
  • the primary object of the invention is to provide a press drive which ensures an exactly corresponding movement sequence in every position, which dispenses with a flywheel and which manages with a reduced drive and a lower energy requirement. According to the invention, this is achieved by the characterizing features of claim 1.
  • Such an energy storage device can be used with advantage in general, regardless of how the drive may otherwise be designed, ie by means of a rotary drive or linear drive, and even quite independently of whether two Toggle lever systems are provided or not.
  • a pressure accumulator is particularly suitable, however, if a fluidic drive, such as according to claim 7, is provided anyway.
  • Fig. 2 shows a completely symmetrical drive 1, which is also particularly suitable for a reciprocating rotary drive.
  • Two parallel crank or eccentric shafts (only one of which is shown schematically as drive 1), which are designed as flywheel-free motor shafts of a hydraulic or electric motor, ensure the drive of the toggle levers 29, 29 '. Care is taken to ensure that the movement of the two shafts or drives 1 takes place synchronously with one another, so that the movement of the two toggle levers 29, 29 'is uniform.
  • the synchronization can be electrical, which is easily possible due to the pulse-dependent position of the rotor of synchronous or asynchronous motors. Additionally or alternatively, mechanical coupling can also be provided. Even a single crankshaft (drive 1) could even be provided.
  • FIG. 2 The construction shown in FIG. 2 is also particularly suitable for a to-and-fro rotary drive because a certain simplification results from the fact that for two strokes of the tool carrier 5, the angle ⁇ is on both sides of the crank dead center T (corresponding to the top dead center) the tool holder 5) is passed through, which is favorable in terms of smoothness and energy consumption.
  • the movement to both sides must then be limited by a corresponding limiter device, as will be discussed with reference to FIG. 1.
  • Two toggle levers 29, 29 ' form a scissor system for a straight guide construction. They are hinged at one end via a bearing 26, 26 'to a balance weight 31. On the other hand, the toggle levers 29, 29 'are articulated on a tool carrier 5. To support the guide are the tool holder Assigned to 5 columns 106 in guides 30, and analogously, a guide column 32 can pass through an opening 33 in a counterweight 31 (FIG. 5).
  • a link 37 or 37' is pivotable, which theoretically represents only a pressure member, but is exposed to both tensile and compressive loads in view of the high stroke frequencies of the punch press.
  • a guide column 32 is provided for the counterweight 31. It cannot be seen in more detail that this column 32 is fastened to a frame in holding bushes 39.
  • the frame has a recess to enable the free movement of the weight 31 up and down.
  • adjusting device 22 is indicated, through which not only the upper reversal point of the movable tool carrier 5, but also its bottom dead center is adjustable in height.
  • Another adjustment device can e.g. be formed as follows: nuts with a thread are arranged above guide columns, the frame being provided with guide sleeves, each of which has a bore for receiving the guide columns.
  • the sleeves can have an approximately rectangular outer contour, the longer side of which runs in one plane, the shorter side, however, perpendicular to this plane.
  • a cutout thus penetrates at least one outer surface of the sleeves, for example only the front surface, but possibly also the rear surface, so that the nuts partially protrude outwards and can be actuated from the outside.
  • the height of the frame can now be adjusted by turning the nuts, the nuts of course having to be adjusted in the same direction and by the same amount.
  • they can have a common adjustment drive which, for example, has a toothing with which e.g. a chain, rack or swivel drive is engaged.
  • FIG. 2 An embodiment according to FIG. 2 is preferred for a punch press of extremely high punch frequency.
  • the connecting rods 104, 104 ' are relatively long and overlap or overlap each other during their passage through the dead center T.
  • the two connecting rods 104, 104' are axially offset from one another.
  • crankshaft drive 1
  • crank pin connecting rod 4
  • crank pin 3 On the opposite. lower end of the connecting rod 4, a movable tool carrier is shown directly connected for the sake of simplicity; in practice, a toggle lever system is also connected in between.
  • the tool carrier 5 can be moved up and down along guide columns 6 which are connected to a stationary tool carrier 7.
  • Both tool carriers 5, 7 are designed in a manner known per se, not shown here, for fastening tools 8 indicated by dash-dotted lines. These tools 8 lie against one another in the lowest dead center position of the crank pin 3, or have the greatest approximation to one another.
  • An eccentric shaft (drive 1) can be driven by an electric motor 9.
  • the shaft 1 is dimensioned in terms of its diameter or provided with a wheel of such a diameter that a rotation of 180 ° from the bottom dead center position shown results in the maximum possible stroke in this punch press, which is only required for certain tools is, whereas in most cases a smaller stroke is sufficient.
  • the motor 9 operating in motor and braking mode is provided with a reversing device 10 for the direction of rotation. In this way, it is possible to reverse the direction of rotation of the shaft (drive) 1 at a certain point.
  • the motor 9 has a rotor, the position of which is determined by the respective number of pulses that are supplied to the motor 9.
  • Such motors are either stepper motors or - which is preferred because of the better drive properties - are synchronous or asynchronous motors.
  • the motor 9 is preceded by a limiter device 11, via which a predetermined number of pulses can be fed to it.
  • a pulse generator 12 is provided for delivering this predetermined number of pulses.
  • Such an assembly can be constructed from mechanical-galvanic elements (e.g. a switch cam which interacts with a switch and is stopped after the predetermined number of pulses), it can be a relay technology structure, or - as shown - a clock generator 13, to which a counter stage 14 is connected.
  • the counter stage 14 has in the usual way a number of only indicated outputs and can be a decade counter or a binary counter. One of its outputs, the output nx, is connected to a shutdown input A of the limiter device 11. This is the case if the counter 14 is a decadal counter, whereas in the case of a binary counter, the number corresponding to the predetermined number of pulses is logically L at some outputs and "O" at other outputs. In the latter case, it is necessary to connect all outputs to the limiter device 11 via an AND gate, for example all outputs with the signal "L” directly, all outputs with the signal "O” via an inverter, so that the AND gates are only supplied "L” signals when the predetermined number is reached.
  • the motor current of the motor is switched off via the output nx.
  • the arrangement can now be such that a braking device in the form of a braking circuit 15 is switched on at the same time, by means of which the motor 9 is switched over to generator operation.
  • an output ny of the counter 14 which is connected on the one hand, expediently via a gate circuit 16, to the braking device 15, and on the other hand to a reset input R, which causes the counter 14 to be switched back to zero and then with a new count begins.
  • the last output of the counter 14, ie the output ny which corresponds to the highest number and thus the predetermined top position of the tool carrier 5, also connected to the reversing device 10 in the form of a reversing stage, so that when the counter 14 continues to count, the same distance from the eccentric shaft is now covered in the opposite direction.
  • an adjusting device is therefore expediently provided.
  • such an adjustment device can be created in that the outputs of the counter 14 can optionally be connected to the stages 10, 11 and 15, so that they are activated depending on the respectively connected output and the corresponding counter reading. It would also be possible to provide a plurality of counting stages instead of a single counter 14, each counting stage corresponding to a different maximum counting value and thus a different angle ⁇ .
  • the shutdown input A of the limiter device 11 can be connected to various outputs of the counter 14 via an adjusting device 17 designed as a sliding contact, and analogously the reset input R, the input of the reversing device 10 and the braking device 15 can be connected via one another (not shown) sliding contact can be optionally connected to different outputs.
  • the gate circuit 16 has already been mentioned, one input of which is formed by the output ny of the counter stage 14.
  • the other input may be led via a switch tongue S1 connected to the main switch 18 for the motor current of the motor 9, or a switch tongue S2 may be connected to this main switch 18 (in a manner not shown) via which the clock generator 13 also connects to the motor 9 can be switched on.
  • the braking device 15 can also be tilted into its braking state only when the motor 9 is switched on.
  • the circuit shown creates a reciprocating drive by means of which the top dead center of the tool carrier 5 can be easily adjusted. It goes without saying that this drive itself can be replaced by equivalent drives, although the drive shown or described is also characterized by low mass and high performance, primarily because of the good interaction with the energy store.
  • the various stages 10, 11 and 15 are controlled by an electronic program control unit, but other known program control units can of course also be used for this purpose. For example, a microprocessor could be provided for this purpose, which could then possibly take on additional control tasks.
  • the input of the desired angle ⁇ can then be carried out particularly easily using a keyboard device.
  • a program control unit can also include such sensors in the form of position sensors.
  • a switch S3 can interrupt the control of the braking device 15 via the counter 14.
  • a selection device 19 is also provided, to which three switching positions are assigned. In the position I shown, the function takes place in the manner described above; in position II it is not possible to reverse the direction of rotation, i.e. the motor 9 rotates continuously in one direction, ie makes at least one rotation through 360 °.
  • the adjusting device 17 designed as a sliding contact is placed in a position 20 for this function, so that the stage 11 can no longer receive a switch-off signal, while on the other hand it continues (as in the function according to position I of the adjusting device 19) via a terminal B with the Clock generator 13 is connected and can receive pulses from it.
  • This circuit with terminal B can, however, possibly prevent the clock frequency of the clock generator 13 from being matched to the mains frequency or even being synchronized, so that the number of pulses supplied to the motor 9 - in accordance with that of the clock generator 13 - actually comes from the network.
  • the limiter device 11 is connected to a position transmitter switch S4.
  • Another position transmitter switch S5 is arranged upstream of the switch S4 at an adjustable distance.
  • both switches S4, S5 are connected to one another by a bracket 21 and can be displaced together along an adjustment device 22, designed as a guide indicated by a broken line, for adjusting the angle ⁇ .
  • the drive 1 is provided with a radial stop extension 23 which actuates the switch S5 in the course of its travel and via him a signal on the one hand to a shutdown input A '(it can also be A) of the limiter device 11 for the motor 9 to interrupt its power supply, on the other hand also brings the braking device 15 for switching the motor 9 to generator operation.
  • the braking device 15 switches in the manner of a monostable multivibrator after the motor 9 has come to a standstill, i.e. when this no longer delivers current, it automatically switches back to "motor operation" without the need for a separate signal.
  • a monostable multivibrator after the motor 9 has come to a standstill, i.e. when this no longer delivers current, it automatically switches back to "motor operation" without the need for a separate signal.
  • it can be equipped with a latching circuit for this purpose, which is powered by a relay (which is fed by the current of the motor 9) is held long until this current drops to zero.
  • crankshaft may move a little further under the influence of the inertial forces, although this distance can be very short, especially if a mechanical brake is provided in addition to the electrical braking device 15. If the crank pin 3 is fastened on a disk which can be rotated about the axis 2, a disk brake, which is magnetically controlled and triggered via the switch S5 (or the output ny of the counter 14) can act on this disk.
  • the stop extension 23 may strike an adjustable stop 24 at the end of its movement, while at the same time the direction of rotation is reversed via the switch S4.
  • a similar arrangement with two switches can then be provided for the backward movement, not shown, which correspond to the switches S4, S5.
  • a linear drive of the same kind can also be used, in particular with fluidic (usually hydraulic) cylinder-piston units 101, 101 ′; 301 (Fig. 3-5) can be used, which also results in a wobble-free movement characteristic when the two drives are synchronized with one another.
  • the movable tool carrier 5 is guided with the aid of frame-fixed guides 30, 30 'and guide columns 106 with narrow tolerances.
  • PV e.g. a proportional valve
  • control line 60 opens into the cylinders 101, 101 'on the side facing away from the piston rod 404 or 404', but control would also be possible on the opposite side or on both sides.
  • a connection for a pressure accumulator 200 is provided on the other side.
  • a balance weight 31 which is practically indispensable in high-frequency punching presses with a stroke frequency of approximately 400 strokes / min, can be attached to the extensions of the legs 228, 228 ', i.e. So be attached to the segments 151, 151 ', conveniently via the handlebars 37, 37', similar to the case in Fig. 4. or 5 with the upwardly extending extensions of the fixed articulated legs of the toggle lever.
  • the control valve PV can be of a type known per se and there are numerous valves for such purposes on the market. Not only can this be an even, wobble-free one Achieve motion sequence, but it can also be varied by varying the inflow amount of hydraulic medium during the stroke, so as to obtain a desired overall characteristic of the movement. This is particularly important if smooth punch-cut edges are to be achieved, for which numerous coupling gears have been proposed in fine punching technology, which are not required in the drive design shown.
  • FIG. 4 and 5 illustrate how fluidic energy storage 201, 201 'can still be used for this purpose, which on the one hand can be easily formed with a small mass, on the other hand do not require a clutch.
  • the pressure accumulators 201, 201 ' have in the usual way compressed gas-filled cylinder spaces 61 and 62 (Fig. 4).
  • the gas is compressed in rooms 61 and expanded in rooms 62 when the pistons of drives 101, 101 'move from the center into the interior of the machine.
  • the compressed gas then drives the toggle levers or the tool carrier 5 again when relaxing in the opposite direction.
  • energy storage 201, 201 ' is not limited to the arrangement of fluid drives or linear drives; rather, they can also be used with advantage in general for rotary drives, ie both for drives according to the previously discussed embodiments, as well as with any rotary drives. Such energy stores are particularly recommended for a linear drive.
  • counterweight 31 is only shown symbolically here and, of course, could of course be arranged as desired.
  • This drive 301 has only a single piston rod 704, but two rods 604, 604 'are mechanically coupled by a pivot pin 63, so that a synchronous drive of the toothed segments 151, 151' is secured from this side.
  • the toothed segments 151, 151 ' here also ensure the synchronous movement during the stroke movement supported by the pressure accumulators 201, 201'.
  • the top dead center is preferably reached by pivoting the toggle levers to the left and right from the extended position (bottom dead center).
  • each tool carrier is generally rectangular in plan view, instead of two toggle levers, four of them can be provided, for example, which each engage one corner of the rectangle or in the area thereof.
  • FIGS. 3 to 5 it is also possible in the case of FIGS. 3 to 5 to provide arc-shaped cross-head guides instead of the straight guides.
  • a horizontal arrangement of the guide columns 6 would also be conceivable, which is why the terms “above” or “below” used in the description are only of relative importance and relate only to the examples, especially since an inverted arrangement would also be possible.
  • step circuit shown in Fig. 1 is only an example.
  • incremental encoders can be attached to the respective shaft and used to form a feedback signal.
  • Another possibility is to use hydraulic motors for the reciprocating drive, the work force of the tool holder also being able to be set by adjusting the pressure.
  • the current supplied to the electric motors can be adjustable to adjust the work force.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Materials Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Punching Or Piercing (AREA)
  • Presses And Accessory Devices Thereof (AREA)

Abstract

Pour permettre l'entraînement de deux leviers coudés ou genouillères (29, 29') d'une presse, telle que notamment une presse à découper à haute fréquence effectuant au moins 400 coups par minute, on prévoit deux dispositifs d'entraînement séparés mais synchronisés l'un par rapport à l'autre (101, 101') destinés à assurer un mouvement uniforme sans oscillation du porte-outil (5). Les dispositifs d'entraînement (101, 101') peuvent avoir la forme d'entraînements rotatifs ou linéaires et sont utilisés pour entraîner les leviers coudés ou genouillères (29, 29') durant une partie au moins de leur mouvement. Un accumulateur d'énergie (200) assure une faible consommation d'énergie, dès lors qu'il emmagasine l'énergie de freinage et la redistribue au dispositif d'entraînement durant l'accélération.

Claims (11)

1. Entraînement de presse pour deux porte-outils (5, 7) mobiles l'un par rapport à l'autre dont l'un au moins peut être entraîné par au moins deux genouillères (29, 29′; 129, 129′; 229, 229′) avec deux points morts à chaque fois, au moins une tige (4; 104, 104′; 404, 404′; 504, 504′; 604, 604′; 704) pouvant transmettre de l'énergie d'entraînement à chacune de ces genouillères (29, 29′; 129, 129′; 229, 229′) à partir d'un support d'énergie d'entraînement pour chacune d'elles, l'un des points morts des genouillères (29, 29′; 129, 129′; 229, 229′) déterminant le rapprochement le plus important des deux porte-outils (5, 7) mobiles l'un par rapport à l'autre, les genouillères (29, 29′; 129, 129′; 229, 229′) se pliant à chaque fois dans des directions opposées, et les supports d'énergie d'entraînement étant synchronisés entre eux par l'intermédiaire d'un dispositif de synchronisation, caractérisé par le fait que les supports d'énergie d'entraînement comprennent un accumulateur d'énergie formé par un fonctionnement à quatre quadrants électrique ou par un accumulateur de pression qui cède une énergie accumulée pour accélérer les masses, ou, respectivement, qui la prend à l'alimentation en énergie, et qui, lors du freinage des masses, emmagasine l'énergie du freinage, ou, respectivement la ramène à l'alimentation en énergie.
2. Entraînement selon la revendication 1, caractérisé par le fait que les accumulateurs d'énergie comprennent un entraînement en va-et-vient (1; 101, 101′; 301).
3. Entraînement selon la revendication 2, caracterisé par le fait que chaque entraînement (1; 102) comprend à chaque fois un arbre qui peut tourner - grâce à au moins un dispositif limiteur (11, respectivement S4, S5), et de préférence à deux - alternativement dans l'une ou l'autre seulement des directions, sur une zone angulaire prédéterminée (α), et des deux côtés du point mort qui correspond au rapprochement le plus important des porte-outils (5, 7), un dispositif de réglage (17, respectivement 22) étant associé de préférence au dispositif limiteur (11, respectivement S4, S5), et le dispositif limiteur (11, respectivement S4, S5) comportant le cas échéant un dispositif de freinage (15), en particulier électrique et/ou mécanique.
4. Entraînement selon la revendication 2 ou 3, caractérisé par le fait qu'il est constitué par au moins un moteur électrique reversible (9) - en particulier synchrone ou asynchrone - qui comporte un induit dont la position dépend d'impulsions et un générateur d'impulsions (12) auquel est associé de préférence un dispositif inverseur (10) pour changer le sens de rotation.
5. Entraînement selon la revendication 4, caractérisé par le fait que le générateur d'impulsions (12) comporte un dispositif de réglage (17) destiné à modifier le nombre des impulsions, et de préférence un compteur (14) en amont duquel est avantageusement montée une horloge (13).
6. Entraînement selon la revendication 4, caractérisé par le fait que le dispositif inverseur (10) comporte un dispositif de commutation destiné à faire passer le moteur électrique (9) au fonctionnement en générateur en vue de son freinage, un dispositif sélecteur (19) étant de préférence relié au dispositif de commutation pour le faire tourner si on le souhaite dans un seul sens seulement, et sur 360° complets à chaque fois.
7. Entraînement selon la revendication 2 ou 3, caractérisé par le fait qu'il est prévu au moins un moteur hydraulique réversible - associé à l'accumulateur de pression (200; 201, 201′) - ou un ensemble cylindre-piston à fluide (101, 101′; 301), en particulier hydraulique, qui peut être commandé par l'intermédiaire d'au moins un dispositif à vanne (PV).
8. Entraînement selon l'une des revendications précédentes, caractérisé par le fait que le support d'énergie d'entraînement ou, respectivement, l'entraînement (101, 101′; 102; 301) est disposé entre deux genouillères (29, 29′; 129, 129′; 229, 229′) et au milieu de celles-ci.
9. Entraînement selon l'une des revendications précédentes, caractérisé par le fait que les points d'articulation des deux genouillères disposées symétriquement (29, 29′) sont guidés au moyen de têtes de bielle (25, 25′) avec lesquels l'accumulateur d'énergie est en prise.
10. Entraînement selon l'une des revendications précédentes, caractérisé par le fait que les genouillères (129, 129′; 229, 229′) sont montées pour l'essentiel en un point fixe dans une région d'une branche (128, 128′; 228, 228′) de la genouillère, et qu'elles sont reliées par l'extrémité libre de l'autre branche (127, 127′; 227, 227′) à l'un des deux porte-outils (5), et par le fait qu'au moins l'une des caractéristiques suivantes est réalisée:
a) La branche (128, 128′; 228, 228′) qui est articulée pour l'essentiel en un point fixe est prolongée au-delà de son point d'articulation fixe (126, 126′), et elle est en prise avec un contre-poids (31) qui est mobile le long d'un guidage rectiligne, en particulier vertical, par exemple d'une colonne de guidage (32), avantageusement par l'intermédiaire d'un bras articulé (37, 37′; 137, 137′);
b) Les branches (228, 228′) des genouillères qui sont articulées en un point fixe sont reliées à un contrepoids commun (31), les points d'attaque (138, 138′) des genouillères (129, 129′; 229, 229′) étant disposés symétriquement par rapport à son centre de gravité;
c) Les paliers fixes (126, 126′) et les supports d'énergie d'entraînement ou, respectivement, les entraînements (101, 101′; 301) sont disposés sur un cadre commun qui peut être déplacé au moyen d'un dispositif de déplacement afin de regler le rapprochement le plus important des deux porte-outils (5) - dans leur direction de déplacement.
11. Entraînement selon l'une des revendications précédentes, comprenant des tiges (104, 104′) réalisées sous la forme de bielles sur un entraînement tournant, et un ou deux arbres à came ou à excentrique (102), caractérisé par le fait que les tiges (104, 104′) sont superposées, décalées axialement et symétriques par rapport à un plan qui passe par le ou les arbres à came ou à excentrique de l'entraînement tournant (102), en étant de préférence reliées à chaque fois à l'arbre à came ou à excentrique qui est opposé à la genouillère correspondante (29, 29′), et dont un au moins, mais en particulier les deux, est réalisé ou, respectivement, sont réalisés directement - de préférence sans volant - sous la forme d'arbre(s) moteur(s), avantageusement d'un moteur hydraulique ou électrique (9).
EP88901014A 1987-02-03 1988-02-03 Entrainement pour presse Expired - Lifetime EP0300000B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88901014T ATE65052T1 (de) 1987-02-03 1988-02-03 Pressenantrieb.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH364/87 1987-02-03
CH36487 1987-02-03

Publications (2)

Publication Number Publication Date
EP0300000A1 EP0300000A1 (fr) 1989-01-25
EP0300000B1 true EP0300000B1 (fr) 1991-07-10

Family

ID=4185343

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88901014A Expired - Lifetime EP0300000B1 (fr) 1987-02-03 1988-02-03 Entrainement pour presse

Country Status (5)

Country Link
US (1) US4920782A (fr)
EP (1) EP0300000B1 (fr)
JP (1) JPH01502011A (fr)
DE (1) DE8890008U1 (fr)
WO (1) WO1988005724A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004051993A1 (de) * 2004-10-25 2006-06-14 Müller Weingarten AG Antriebssystem einer Umformpresse
DE102008038264A1 (de) * 2008-08-15 2010-02-18 H & T Produktions Technologie Gmbh Elektrisch angetriebene Presse

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2659717A1 (fr) * 1990-03-19 1991-09-20 Kodak Pathe Procede et dispositif pour animer une surface d'un mouvement de va-et-vient dans un plan.
US5070719A (en) * 1990-10-16 1991-12-10 Amp Incorporated Tooling control mechanisms for stamping and forming die assemblies
JP2534944B2 (ja) * 1991-09-24 1996-09-18 アイダエンジニアリング株式会社 プレス機械
JP3318071B2 (ja) * 1993-08-25 2002-08-26 株式会社三共製作所 機械式プレス装置
JP3288494B2 (ja) * 1993-08-25 2002-06-04 株式会社三共製作所 機械式プレス装置
JP3353959B2 (ja) * 1993-08-25 2002-12-09 株式会社三共製作所 機械式プレス装置
EP0765735B1 (fr) * 1995-09-27 2001-04-11 Bruderer Ag Presse poinçonneuse à genouillère
DE19918700A1 (de) * 1999-04-26 2000-11-02 Mueller Weingarten Maschf Hydromechanischer Pressenantrieb
JP2002205197A (ja) * 2001-01-11 2002-07-23 Yamada Dobby Co Ltd プレス機の動力伝達装置
DE102006034201A1 (de) * 2006-07-24 2008-02-07 Siemens Ag Presse
US8020727B2 (en) * 2006-10-18 2011-09-20 Meritool Llc Powered dispensing tool and method for controlling same
US7980172B2 (en) * 2007-05-29 2011-07-19 Gemma Bernabe Closure mechanism and waste compaction system including same
DE102007054769A1 (de) * 2007-11-16 2009-05-20 Bosch Mahle Turbo Systems Gmbh & Co. Kg Stellantrieb für bidirektionales Stellglied
US7682292B1 (en) * 2009-01-29 2010-03-23 Giant Manufacturing Co., Ltd. Flywheel-type variable resistance generating device for an exercising apparatus
DE102009007339B4 (de) * 2009-02-04 2023-09-21 Robert Bosch Gmbh Widerstandsschweißzange und Verfahren zu deren Betrieb
EP2258498B1 (fr) * 2009-06-03 2012-12-26 Feintool Intellectual Property AG Presse mécanique destinée à couper fin, déformer et/ou imprégner des pièces usinées
CN103121294A (zh) * 2013-02-06 2013-05-29 宁波精达成形装备股份有限公司 顶置油缸曲轴肘杆式四柱压力机
CN103434166B (zh) * 2013-08-14 2015-07-08 浙江帅锋精密机械制造有限公司 一种高速精密冲床
US9908171B2 (en) 2015-11-25 2018-03-06 Btm Company Llc Linkage press machine
EP3976380B1 (fr) * 2019-05-27 2023-04-26 Bobst Mex Sa Presse à platine avec mécanisme de commutation

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE547236C (de) * 1930-10-26 1932-03-19 Siemens Schuckertwerke Akt Ges Elektrisch angetriebene Schmiedepresse
US2087811A (en) * 1934-06-15 1937-07-20 Hydraulic Press Corp Inc Press
US2224968A (en) * 1935-05-14 1940-12-17 Klocke William Hydromechanical press
CH227843A (de) * 1941-07-16 1943-07-15 Weingarten Ag Maschf Schwungradantriebseinrichtung für Pressen, Stanzen und ähnliche Arbeitsmaschinen.
US2633094A (en) * 1948-12-02 1953-03-31 Bliss E W Co Power-operated press device
US2633765A (en) * 1949-02-23 1953-04-07 Clearing Machine Corp Forming press
GB807760A (en) * 1955-06-24 1959-01-21 William Frank Golding Improvements in or relating to power presses
US3000429A (en) * 1956-06-22 1961-09-19 Studebaker Packard Corp Machine for prestressing and molding reinforced plastic members
DE1502288A1 (de) * 1964-07-21 1969-03-20 May Pressenbau Gmbh Kniehebelpresse
US3682029A (en) * 1970-04-13 1972-08-08 Schwabe Inc Herman Balanced and double action cutting apparatus
DE2111054A1 (de) * 1971-03-09 1972-09-14 Alois Steinmetz Kniehebel-Press-Stanze mit von den Mittelfuehrungen unabhaengiger,paralleler Schliessbewegung
DE2501748C3 (de) * 1975-01-17 1983-11-03 L. Schuler GmbH, 7320 Göppingen Schnittpresse mit Kniegelenkantrieb
JPS51106278A (ja) * 1975-03-15 1976-09-21 Kyori Kogyo Co Ltd Puresuki
DE2804390A1 (de) * 1978-02-02 1979-08-09 Schuler Gmbh L Vorrichtung fuer einen intermittierenden betrieb bei einer nutenstanze
DE2912927A1 (de) * 1979-03-31 1980-10-16 Schuler Gmbh L Antrieb fuer eine presse
DE2925416C2 (de) * 1979-06-23 1983-02-24 Werner Ing.(Grad.) 6460 Gelnhausen Leinhaas Kniehebel-Blechschneidepresse
DE2934286C2 (de) * 1979-08-24 1984-06-14 L. Schuler GmbH, 7320 Göppingen Mehrpunkt-Pressenantrieb
US4350091A (en) * 1980-01-15 1982-09-21 J. E. Myles, Inc. Crank press with hydraulic transmission
ATE8756T1 (de) * 1981-02-11 1984-08-15 L. Schuler Gmbh Pressenantrieb.
JPS6029599A (ja) * 1983-07-26 1985-02-14 防衛庁技術研究本部長 焼尽薬莢用の燃焼性筒体の製造方法
DE3517492A1 (de) * 1984-11-05 1986-05-07 Werner Ing.(Grad.) 6460 Gelnhausen Leinhaas Kniehebel-blechschneidepresse, bestehend aus einem pressenstaender und einem pressenstoessel

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004051993A1 (de) * 2004-10-25 2006-06-14 Müller Weingarten AG Antriebssystem einer Umformpresse
DE102004051993B4 (de) * 2004-10-25 2008-11-27 Müller Weingarten AG Antriebssystem einer Umformpresse
DE102008038264A1 (de) * 2008-08-15 2010-02-18 H & T Produktions Technologie Gmbh Elektrisch angetriebene Presse

Also Published As

Publication number Publication date
DE8890008U1 (de) 1990-07-12
JPH01502011A (ja) 1989-07-13
EP0300000A1 (fr) 1989-01-25
WO1988005724A1 (fr) 1988-08-11
US4920782A (en) 1990-05-01

Similar Documents

Publication Publication Date Title
EP0300000B1 (fr) Entrainement pour presse
DE102004009256B4 (de) Mechanische Mehrservopresse
DE3044083C2 (de) Stanzeinrichtungen für Stanzautomaten zum Stanzen von Bögen aus Papier, Pappe u. dgl.
DE19521050C2 (de) Kniehebel-Antriebsvorrichtung
DE102012210678A1 (de) Handwerkzeugmaschine
DE803142C (de) Kurbelgetriebe
DE881143C (de) Hydraulische Schmiedepresse
US4307599A (en) Stamping press
EP1754595B1 (fr) Module d'entraînement pour presse et procédé pour fournir une gamme de presses
DE2906107A1 (de) Stanzpresse
DE2756096C2 (de) Transporteinrichtung zur schrittweisen Beförderung von Gegenständen, insbesondere von Werkstücken bei Pressen
DE2344529A1 (de) Anordnung zur dynamischen auswuchtung einer hochgeschwindigkeits-presse
EP0635320B1 (fr) Serre-flan pour presses à simple effet en particulier pour presses mécaniques et presses de transfert
DE3024565C2 (de) Drehantreibbare Vorrichtung, insbesondere Rundschalttisch
EP0718092B1 (fr) Presse d'estampage de monnaie
DE854748C (de) Durch Muskelkraft anzutreibende Hebelpresse
DE2742041A1 (de) Vorrichtung zum auswerfen von werkstuecken aus matrizen
EP0351632A2 (fr) Dispositif d'entraînement pour une machine à découper travaillant par intermittence
AT210716B (de) Einrichtung zum Antrieb des Werkzeugträgers einer Schere, Presse od. dgl.
DE3526410C1 (de) Antriebsvorrichtung zur Umwandlung einer Rotationsbewegung in eine Oszillationsbewegung mit verschwenkbarem Joch
DE3631483C2 (fr)
AT377714B (de) Schlagpresse
DE400572C (de) Kolbenpumpe
DE333275C (de) Doppelsteuerung fuer ein- oder zweiseitig wirkende Schuettelrutschenmotoren
DE124087C (fr)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19880930

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT CH DE FR GB IT LI

ITCL It: translation for ep claims filed

Representative=s name: JACOBACCI CASETTA & PERANI S.P.A.

GBC Gb: translation of claims filed (gb section 78(7)/1977)
EL Fr: translation of claims filed
17Q First examination report despatched

Effective date: 19900406

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT CH DE FR GB IT LI

REF Corresponds to:

Ref document number: 65052

Country of ref document: AT

Date of ref document: 19910715

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3863599

Country of ref document: DE

Date of ref document: 19910814

ITF It: translation for a ep patent filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GR

Payment date: 19940218

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19950130

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19950203

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19950223

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19950317

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19950323

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19960203

Ref country code: AT

Effective date: 19960203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19960229

Ref country code: CH

Effective date: 19960229

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19960203

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19961031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19961101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050203