EP0300000A1 - Entrainement pour presse. - Google Patents

Entrainement pour presse.

Info

Publication number
EP0300000A1
EP0300000A1 EP88901014A EP88901014A EP0300000A1 EP 0300000 A1 EP0300000 A1 EP 0300000A1 EP 88901014 A EP88901014 A EP 88901014A EP 88901014 A EP88901014 A EP 88901014A EP 0300000 A1 EP0300000 A1 EP 0300000A1
Authority
EP
European Patent Office
Prior art keywords
drive
energy
drive according
toggle
carriers
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.)
Granted
Application number
EP88901014A
Other languages
German (de)
English (en)
Other versions
EP0300000B1 (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

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.
  • the inventive design of the machine with the synchronized double knee levers and the mass balance thus created a new, electronically controllable type of press.
  • the press machine described according to the invention has the following advantages over the prior art:
  • an infinitely variable ram stroke can be selected due to the adjustability of the swivel angle or piston travel;
  • drive energy carrier in the present description encompasses everything that drive energy is capable of delivering, and in fact only in a partial area of the movement, i.e. also the energy storage.
  • Such an energy storage device can be used with general advantage, regardless of how the drive may otherwise be designed, ie by means of a rotary drive or linear drive, or even completely 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 8, is provided anyway.
  • FIG. 1 shows a basic circuit diagram with an electric drive, the adjustment possibilities that are presented are also shown;
  • FIG. 2 shows a first embodiment with two completely symmetrical drives for both sides of a movable tool carrier, a cross-head guide at the articulation points of the two toggle levers additionally ensuring a smooth, wobble-free movement;
  • FIG. 3 shows a first exemplary embodiment for realizing the invention with the aid of centrally arranged fluidic linear drives (cylinder-piston units);
  • Fig. 4 and 5 further variants with differently placed energy storage.
  • the figures are described together.
  • the same parts have the same reference numbers. Repeating parts are not shown in some cases (eg energy storage in Fig. 2).
  • FIG. 2 shows a completely symmetrical drive 1, which is also particularly suitable for a to-and-fro rotary drive.
  • Two parallel crankshafts or eccentric shafts (only one of which is shown schematically as drive 1), which are designed as flywheelless motor shafts of a hydraulic or electric motor, drive the toggle levers 29, 29 '. It is important 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.
  • 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) ⁇ point of the tool carrier 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 articulated at one end to a balance weight 31 via a respective bearing 26, 26 '. On the other hand, the toggle levers 29, 29 'are articulated on a tool carrier 5. To support the leadership, the tool carrier 5 column 106 associated with guides 30 in r and in analogy to this, a guiding column 32 has an opening 33 in a Aus ⁇ equilibrium enforce 31 (Fig.5).
  • the upper legs 128, 128 '; 228.228' of the toggle lever 129, 129 '; 229, 229 ' can be extended beyond the fixed pivot point 126, 126' and have a short extension arm 36, 36 '.
  • a link 37 or 37 ' can be pivoted on each of these arms 36 and 36', which in theory represents only one link, 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. In order to enable the free movement of the weight 31 up and down, the frame has a recess.
  • an adjusting device 22 is indicated, by means of which not only the upper reversal point of the movable tool carrier 5 but also its lower dead center can be adjusted in height.
  • a further adjustment device can e.g. be constructed 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 extends in a 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.
  • a configuration according to FIG. 2 is preferred for a punching press of extremely high punching frequency.
  • the connecting rods 104, 104 ' are of relatively long design and overlap or overlap one another 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 3 a connecting rod 4 being articulated on a crank pin 3.
  • a movable tool carrier is shown directly connected for the sake of simplicity; in practice, a toggle lever system is also interposed here.
  • 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 are located in the bottom dead center position of Kurbel ⁇ pin 3 to each other or have the closest proximity an ⁇ other.
  • An eccentric shaft (drive 1) can be driven by an electric motor 9.
  • the shaft 1 is dimensioned with respect to its diameter or provided with a wheel of such a diameter that a rotation through 180 ° from the bottom dead center position shown results in the maximum possible stroke with this punch press, which is only possible with certain Tools is, whereas in most cases a smaller stroke is sufficient.
  • the motor 9 operating in motor and brake operation is equipped with a reversing device 10 for the Provide 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.
  • a limiter device 11 is connected upstream of the motor 9, 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 made up of mechanical-galvanic elements (e.g. a switch cam that interacts with a switch and is stopped after the predetermined number of pulses), it can be a relay technology design, or - as shown - a clock generator 13, to which a counting stage 14 is connected.
  • the counter 14 has a number of in the usual way. only indicated outputs and can be a decadal counter or a binary counter. One of its outputs, the output nx, is connected to a shutdown input A of the limiter device 11.
  • the motor current of the motor is switched off via the output nx.
  • the arrangement can now be such that at the same time a braking device in the form of a brake circuit 15 is switched on, 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 counter 14 to be switched back to zero and then to start a new count.
  • 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 to this, the reset input R, the input of the reversing device 10 and the Braking device 15 can optionally be connected to various outputs via a further sliding contact (not shown).
  • the gate circuit 16 has already been mentioned, one input of which is formed by the output ny of the counter stage 1.
  • 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 can be switched on simultaneously with the motor 9.
  • 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 is understood from this 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 here 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 made particularly simply 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 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, a reversal of the direction of rotation is not possible, ie the motor 9 rotates constantly 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 the terminal B can, however, be omitted if the clock frequency of the clock generator 13 is tuned to the mains frequency or even synchronized, so that the number of pulses supplied to the motor 9 - in accordance with that of the clock generator 13 - borrowed 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 path. and via it gives 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, and on the other hand also the braking device 15 for switching the motor 9 to generator operation brings.
  • 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 self-holding circuit which is held by a relay (which is fed by the current of the motor 9) 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 disc which can be rotated about the axis 2, a disc brake, which is magnetically controlled and triggered via the switch S5 (or the output ny of the counter 14) can act on this disc.
  • 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.
  • An arrangement of the same type with two switches, which correspond to switches S4, S5, can then be provided for the backward movement, not shown.
  • 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 for example 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. thus be attached to the segments 151, 151 ', expediently via handlebars 37, 37', similar to the case with FIGS. 4 and 5 with the upward extensions of the fixedly articulated legs of the toggle levers.
  • 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 a uniform, wobble achieve free movement, but by varying the inflow amount of hydraulic medium during the stroke, the speed can also be changed in order 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 mechanisms have been proposed in fine-punching technology, which are not required in the drive design shown.
  • flywheels which are usually provided in punching machines, in order to provide the necessary energy for the punching cut, have been mentioned several times above.
  • the flywheels were always justified by the fact that the drives can be kept small.
  • the use of the principle according to the invention saves the flywheels without having to oversize the drive, which - because of the mass involved - would have disadvantages with regard to the maximum acceleration of this mass to be achieved.
  • Figures 4 and 5 illustrate; how fluidic energy stores 201, 201 'can still be used for this purpose, which on the one hand can be easily formed with a small mass, and on the other hand do not require a clutch.
  • the pressure accumulators 201, 201 ' have pressure-gas-filled cylinder spaces 61 and 62 in the usual manner (FIG. 4).
  • the gas is compressed in rooms 61 and expanded in rooms 62 when the pistons of the 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 stores 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 driven 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 could, of course, be arranged in any way.
  • this drive 301 has only a single piston rod 704, two rods 604, 604 'are mechanically coupled to it by a pivot pin 63, so that a synchronous drive of the toothed segments 151, 151' is ensured from this side.
  • the tooth segments 151, 151 ' additionally ensure the synchronous movement during the stroke movement supported by the pressure accumulators 201, 201'.
  • the top dead center is preferably reached by swiveling the toggle levers to the left and right from the extended position (bottom dead center).
  • 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 working 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.
  • Back and forth drives (1 01, 1 01 ', 201, 301)
  • Axis geometric crank pin 3' rod (104, 104 ', 404, 404', 505, 504 ', 604, 604 *, 704) tool holder guide columns tool holder tools electric motor

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.
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 true EP0300000A1 (fr) 1989-01-25
EP0300000B1 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)

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Also Published As

Publication number Publication date
DE8890008U1 (de) 1990-07-12
JPH01502011A (ja) 1989-07-13
EP0300000B1 (fr) 1991-07-10
WO1988005724A1 (fr) 1988-08-11
US4920782A (en) 1990-05-01

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