EP2670586B1 - Presse de pressage de pièces - Google Patents

Presse de pressage de pièces Download PDF

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Publication number
EP2670586B1
EP2670586B1 EP12702817.3A EP12702817A EP2670586B1 EP 2670586 B1 EP2670586 B1 EP 2670586B1 EP 12702817 A EP12702817 A EP 12702817A EP 2670586 B1 EP2670586 B1 EP 2670586B1
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EP
European Patent Office
Prior art keywords
chamber
hydraulic
working
delivery device
delivery
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.)
Active
Application number
EP12702817.3A
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German (de)
English (en)
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EP2670586A1 (fr
Inventor
Lothar Bauersachs
Herbert Rüger
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Langenstein and Schemann GmbH
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Langenstein and Schemann GmbH
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Publication of EP2670586A1 publication Critical patent/EP2670586A1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0052—Details of, or accessories for, presses; Auxiliary measures in connection with pressing for fluid driven presses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/12—Drives for forging presses operated by hydraulic or liquid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/18—Drives for forging presses operated by making use of gearing mechanisms, e.g. levers, spindles, crankshafts, eccentrics, toggle-levers, rack bars
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/20—Control devices specially adapted to forging presses not restricted to one of the preceding subgroups
    • 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
    • B30B1/32—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 plungers under fluid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B13/00—Methods of pressing not special to the use of presses of any one of the preceding main groups
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses

Definitions

  • the invention relates to a pressing machine for pressing workpieces.
  • various forming machines presse machines
  • At least one ram with a first pressing tool of the pressing machine is driven by a drive and moved relative to a second pressing tool of the pressing machine, so that between the pressing tools, the workpiece can be deformed by pressing forces.
  • the usually wegG working mechanical presses use mechanical drives, such as servomotor drives, with a variety of translation mechanisms, such as eccentric (eccentric) or toggle (push-pull).
  • the forming force or impact force is dependent on the path or the position of the plunger.
  • the normally force-operated hydraulic presses use a hydraulic drive by means of a hydraulic medium such as oil or water, whose pressure energy is converted by running in hydraulic cylinders piston into mechanical forming work.
  • the ram force corresponds to the product of hydraulic pressure and piston area and is largely independent from the position of the pestle.
  • the hydraulic drive of the piston can be an immediate pump drive with a motor driven variable pump (see eg DE 196 80 008 C1 ) or a hydraulic accumulator drive with accumulator and motor-driven pump to establish the pressure in the pressure accumulator.
  • a motor driven variable pump see eg DE 196 80 008 C1
  • a hydraulic accumulator drive with accumulator and motor-driven pump to establish the pressure in the pressure accumulator.
  • US 4,215,543 describes a method and an apparatus for linear and non-linear operation of a hydraulic press, in particular for control in thermoset processing.
  • US 6,240,758 discloses a hydraulic machine in which hydraulic oil is pumped by means of a hydraulic pump into a cylinder chamber to stimulate a reciprocal mechanism.
  • EP 1 815 972 describes a press line with at least one mechanical press, with at least one variable speed drive motor to vary the press speed during a press cycle.
  • the DE 10 2008 039 011 A1 describes a pressing machine according to the preamble of claim 1.
  • the DE 10 2008 053 766 A1 describes a hydraulic press drive, in particular for a sheet metal or forging press, with a cylinder and a movably mounted in the cylinder between a top dead center and a bottom dead center pressing piston, said pressing piston divides the cylinder into a pressing pressure chamber and a remindhubraum, wherein the pressing pressure chamber with a winningstromumledgebaren compression pressure pump is connected to the hydraulic fluid in the or from the compression chamber pressure can be conveyed or discharged and wherein the return stroke is connected to a recirculation return flow pump, with the hydraulic fluid in or out of the return stroke can be conveyed or discharged, wherein a Control unit is provided, with which the compression pump and the return stroke pump can be controlled independently of each other in dependence on the respective stroke position of the plunger.
  • the object of the invention is now to provide a new pressing machine.
  • Movement course is understood in particular to be a path-time course or speed-time course or speed-route course or force-time course or force-distance course.
  • this includes a plunger 10 and a hydraulic ram drive unit 1 with a hydraulic working piston 2, which is hydraulically movable in an associated, filled with hydraulic medium M hydraulic or working cylinder 3 axially to the working axis A.
  • a in the outer diameter of the inner diameter of the working cylinder 3 adapted and sealed against the inner surface of the working cylinder 3 first piston portion 21 of the working piston 2 separates - at least within leakage tolerances - pressure-tight a lower cylinder chamber 32 of the working cylinder 3 of an upper cylinder chamber 31.
  • a second piston area 22 of the working piston 2 designed here as a piston rod extends in an outer diameter smaller than the first piston area 21, so that only the annular or hollow cylindrical area of the lower cylinder space 32 surrounding the second piston area 22 is filled with the hydraulic medium M.
  • the working piston 2 moves the tappet 10 of the pressing machine 1, which is coupled thereto or fastened, to which a pressing tool 15 is located.
  • the pressing tool 15 can be moved in individual working steps in a pressing movement or in a pressing direction P to a workpiece, not shown, which is located on a second, not shown pressing tool, and in a subsequent return movement away from this or opposite to the pressing direction to be moved.
  • the volume V1 of the upper cylinder space 31 increases and the volume V2 of the lower cylinder space decreases 32 and in the direction opposite to the pressing direction P directed return movement of the working piston 2, the volume V1 of the upper cylinder chamber 31 decreases and increases the volume V2 of the lower cylinder chamber 32 again.
  • the ram drive unit 1 comprises a hydraulically guided in a working chamber, which is designed in the embodiment as a working cylinder 3, which is designed in the embodiment as a drive piston 2, the working chamber in a first, preferably upper, partial chamber and a second preferably lower, sub-chamber separates.
  • the invention is not limited to the embodiment and arrangement of the working chamber and its sub-chambers and of the working piston specified in the exemplary embodiment.
  • a controllable valve 4 is hydraulically connected, which is connected between the upper cylinder chamber 31 and a medium reservoir 5 for the hydraulic medium M.
  • Control connections for opening and closing the valve 4 are denoted by S1 and S2. In the open state of the valve 4, depending on the applied pressure difference, medium M can flow from or into the medium reservoir 5, but not in the closed state of the valve 4.
  • a delivery unit 60 of a servo pump 6 is also hydraulically connected.
  • the hydraulic connection line between the power steering pump 6 and the upper cylinder chamber 31 is designated 36.
  • the feed unit 60 for example a screw conveyor or wisdompumpenrad or an internal gear of an internal gear pump is driven by an output shaft 62 of a servomotor 61 and that in both directions by reversing the direction of rotation of the output shaft 62 of the servo motor 61 as shown.
  • the servomotor 61 is connected via an electrical line 56 to an electrical converter 55, which in turn is connected to the control device 50 via an electrical line 53.
  • a further servo pump 7 is connected via a hydraulic connecting line 37.
  • the feed unit 70 of the second servo pump 7 is connected, which is again driven via an output shaft 62 by a servo motor 71 in the conveying direction reversible, in particular, the servo motor 71 is reversible in its direction of rotation.
  • the servomotor 71 is connected via an electrical line 57 to the inverter 55.
  • connecting line 37 is assigned to the front cylinder chamber 32 Pressure transmitter 14 connected, which is connected via a line 54 to the control device 50.
  • line or control line includes both wired and wireless, such as optical or radio-based, transmission or link routes.
  • a check valve 44 is further connected in each case, which is connected to the medium reservoir 5 and the respective servo pump 6, 7 and 17 protects against idling.
  • the upper cylinder chamber 31 and the lower cylinder chamber 32 each associated with an overload protection device 13 which is connected to the medium reservoir 5 and limit the hydraulic pressure to protect the components exposed to the hydraulic pressure from overloading.
  • FIG. 1 and 2 is the upper cylinder chamber 31 of the working cylinder 3 via a connecting channel 38 with a drive cylinder chamber 82 of a drive cylinder 80 of a drive unit 8 for the working piston 2 in hydraulic communication.
  • Drive cylinder space 82 and connecting channel 38 are also filled with hydraulic medium M.
  • the volume V3 of the drive cylinder space 82 can be changed by a drive piston 81 that is axially movable in the drive cylinder 80 and driven by a connecting rod, in particular a connecting rod, 98 of an eccentric unit 9.
  • the connecting rod 98 mechanically connects the drive piston 81 with an eccentric 92 on an eccentric disk 91.
  • the eccentric axis E of the eccentric 92 runs eccentrically in a radius r about an axis of rotation D of the eccentric disk 91 as it rotates through an angle of rotation ⁇ .
  • a rotary drive for the eccentric 91 is a drive motor 18, in particular a torque motor with a high Torque provided, which, preferably via a gear 19, the eccentric 91 drives in reversible direction of rotation of the drive motor 18 or the transmission 19 and which is connected via an electrical line 58 to the inverter 55.
  • the eccentric axis E lies on a horizontal H through the axis of rotation D and the connecting rod 98 extends substantially vertically between the eccentric 92 and the drive piston 81.
  • the axis of rotation D can also lie exactly vertically above the center of the drive piston 81.
  • the maximum working stroke ⁇ y and the achievable pressing or forming force is dependent on the radius r of the eccentric 92, the selected or set maximum angle of rotation ⁇ and the length of the connecting rod 98, which are also referred to as eccentric parameters below.
  • the area A3 of the drive piston 81 is usually selected to be smaller than the upper surface A1 of the working piston 2, wherein the ratio is determined according to the desired force transmission, which is proportional to the respective surfaces over the substantially equal pressure.
  • the drive unit 8 and the eccentric unit 9 with the drive motor 18 together form a first hydraulic conveyor, which is hydraulically connected on the one hand to the first sub-chamber of the working chamber and on the other hand to the medium storage and reversible in the conveying direction and is a mechanical-hydraulic hybrid drive.
  • This embodiment also provides high forming forces, even at the end of the pressing stroke (due to the variable ratio of sinusoidal kinematics), with increasing forming forces, and is also suitable for upsetting or cold working or holding the ram in certain force loaded positions, e.g.
  • the servo pump 7 is the embodiment for a second hydraulic conveyor, which is hydraulically connected on the one hand to the second sub-chamber of the working chamber and on the other hand to the medium storage and reversible in the conveying direction.
  • the servo pump 6 forms a third hydraulic conveyor, which is hydraulically connected on the one hand to the first sub-chamber 31 of the working chamber and on the other hand to the medium reservoir 5 and reversible in the conveying direction.
  • This formed by the servo pump 6 third hydraulic conveyor is used primarily to compensate for leaks in the hydraulic system, which can only be compensated by the eccentric limited because of the limited stroke, but can also in addition be used to assist or as part of the first conveyor during pressing.
  • a servo pump 17 is provided with a conveyor unit 170, which is again driven via an output shaft 172 by a servo motor 171 which is connected via a line 57 to the inverter 55, and in both conveying directions is operable.
  • the power steering pump 17 is connected to the rear cylinder chamber 31 of the power cylinder 3 on one side via a hydraulic connection line 39 and to the medium reservoir 5 on the other side.
  • a pressure transducer 12 for measuring the pressure in the communication line 39 and thus also the rear cylinder chamber 31, wherein the pressure transducer 12 is again connected via the line 52 to the control device 50.
  • the second conveyor is further formed with the servo pump 7.
  • the third hydraulic conveyor formed with the servo pump 6 is used in this embodiment according to FIG. 3 and 4 now to support the purely hydraulic first conveyor and works in parallel with this during pressing, so that the delivery volumes add up.
  • the axial position of the plunger 10 (or the working piston 2) along the working stroke is measured by means of an associated position measuring device or by means of a Wegmessgebers 11 which is connected via a line 51 to a control device 50.
  • the control device 50 is also connected to a control port S1 of the controllable valve 4 via a line 59 to bring it from the open to the closed or a less wide open state or vice versa.
  • the control device 50 is for checking, in particular for controlling and / or rules and / or monitoring, the workflows and individual components of the forming machine provided.
  • the control device 50 controls (or: controls or regulates) via the inverter 55 the drive motor 18 of the first hydraulic conveyor (8, 9) and the servomotor 71 of the second hydraulic conveyor or servo pump 7 and via the control terminal S1 the controllable hydraulic valve 4 for automatic Control or regulation of the volume flows and pressures as well as the flow direction of the hydraulic medium between the medium reservoir 5 and the first sub-chamber (31) of the working chamber (3) and between the medium reservoir 5 and the second sub-chamber (32) of the working chamber.
  • This control of the volume flows, pressures and flow direction of the hydraulic medium by the control device 50 takes place as a function of the ram position of the ram 10 measured by means of the ram position measuring device 11 and of stored or desired movements of the ram and / or optionally of input information from users.
  • the control device 50 thus operates in a hydraulically open control or control circuit and must control the two conveyors exactly coordinated.
  • the converter 55 preferably comprises an energy buffer, not shown in detail, with which in a process phase generator-generated electrical energy of at least one of the conveyor motors is used and used in a subsequent or later process phase for motor operation of at least one of the conveyor motors, preferably the respective other conveyor motor of the other conveyor.
  • at least one capacitor in an intermediate circuit of the converter or in a capacitor module or kinetic energy store coupled to the intermediate circuit can be used as the energy buffer of the converter.
  • the SINAMICS energy management system (see SIMOTION brochure E20001-A660-P620 from 2008, available at www.siemens.com) can be used as energy buffer storage systems by the company Siemens in the SIMOTION controls for servo presses with direct drive of the ram via servo torque motors. forming technology) adapted for the servo drives (60, 70, 18, 170) of the present hydraulic press machine.
  • the valve 4 is at least partially opened by the control device 50 to a To flow comparatively large volume flow of hydraulic medium M from the medium reservoir 5 in the upper cylinder chamber 31, and the second conveyor, controlled by the control device 50, the servo pump 7, pumping medium M from the lower cylinder chamber 32 into the medium reservoir 5.
  • the servo pump 6 can also re-pump the hydraulic medium M into the upper cylinder chamber 31.
  • control device 50 controls by means of the converter 55 flow rate or delivery pressure of the second conveyor, the servo pump 7, so that the movement of the working piston 2 is braked or accelerated according to a predetermined course of motion, in particular path-time course or speed-time course or speed-distance curve or force-time curve or force-displacement curve, wherein the working piston 2 moves to a predetermined starting point in the predetermined movement within a provided in the course of movement or resulting time.
  • the starting point is basically an arbitrary point between the two end points of the maximum working stroke ⁇ x corresponding to a starting point of the plunger 10 between the two end points of the maximum working stroke ⁇ z of the plunger 10.
  • the idle stroke can also be omitted, ie the starting point for the working stroke are at the top or the total stroke is equal to the working stroke.
  • the movement of the working piston 2 and thus of the plunger 10 during the freewheel or idle stroke is adjusted by the control device 50 with the position values of the position measuring device 11 and adjusted or regulated by controlling the valve 4 and the servo pump 7 and possibly also the servo pump 6.
  • the starting point for the working stroke is a point at which the pressing tool 15 comes into contact with the workpiece and is thus decelerated, which is detected or monitored by the control device 50 by the displacement measurement by means of the position measuring device 11.
  • the torque motor 18 ( FIG. 1 and FIG. 2 ) or servomotor 171 ( FIG. 3 and FIG. 4 ) quiet, the valve 4 is open and the servo pump 7 is working.
  • the freewheeling or Leerhubterrorism the working piston 2 is stopped at the starting point of the working stroke.
  • the control device 50 sets for the pressing stroke on the inverter 55, the torque motor 18 of the eccentric drive 9 ( FIG. 1 and FIG. 2 ) or the servomotor 171 ( FIG. 3 and FIG. 4 ) in operation and closes the valve 4.
  • a working pressure is built up in the rear cylinder chamber 31 of the working cylinder 3, which presses the plunger 10 and the pressing tool 15 attached thereto for the pressing process down into or against the workpiece and presses the workpiece into the second tool.
  • the torque of the torque motor 18 and the eccentric parameters and the power transmission via the drive unit 8 (FIG. FIG. 1 and FIG.
  • the working stroke or pressing travel of the plunger 10 during the pressing stroke can be adjusted by adjusting the angle of rotation ⁇ (stroke adjustment) ( FIG. 1 and FIG. 2 ) or via the angle of rotation of the servomotor 171 (FIG. FIG. 3 and FIG. 4 ).
  • the pressing movement of the working piston 2 or plunger 10 follows again a predetermined course of the control device 50, again the distance measurement via the position measuring device 11 provides information about the position of the plunger 10, via the control device 50 and the inverter 55 for controlling the torque motor 18th ( FIG. 1 and FIG. 2 ) or servomotor 171 (FIG. FIG. 3 and FIG. 4 ) is used, so that the plunger 10 can be driven away controlled.
  • a pressure-dependent control or a travel control with a pressure upper limit. You can for the torque of the respective drive motor Set an upper limit (upper pressure limit) or specify a torque curve path-dependent (pressure-dependent control).
  • the torque input is preferably dynamic, so that the eccentric kinematics is taken into account. At angles ⁇ near the 90 °, ie in the lower point, a higher hydraulic pressure can be generated with the same torque on the torque motor 18.
  • the servo pump 7 is switched to low-torque during the press stroke or the servo motor 71 is not energized, but generates generator due to the flowing through the feed unit 70 from the lower cylinder chamber 32 displaced medium a generator current whose charge or energy is cached by the inverter 55.
  • the servo pump 6 can be switched on / remain to compensate for leaks by refilling hydraulic medium M from the medium reservoir 5 in the upper cylinder chamber 31 (leakage pump).
  • the press stroke is finished, if according to FIG. 2 the plunger 10 reaches its lower end position (bottom dead center).
  • the control device 50 After the plunger 10 has now reached its lower end point, the control device 50 immediately begins the return movement. This first begins with a passive process, the relaxation or decompression process mentioned under point 3, in which the hydraulic medium M is relieved by the compression volume, which is dependent on the compressibility of the medium M.
  • the valve 4 remains closed.
  • the torque motor 18 ( FIG. 1 and FIG. 2 ) or the servomotor 171 ( FIG. 3 and FIG. 4 ) is switched to low torque, ie it can be easily rotated, the decompression of the hydraulic medium M moves the drive piston 81 upwards and the eccentric disc 9, the torque motor 18 is moved in the opposite direction ( FIG. 1 and FIG. 2 ) or the servo pump 170 is in opposite Direction rotated together with the servo motor 171 ( FIG. 3 and FIG. 4 ) and energetically supplies energy to the inverter 55 and its energy buffer.
  • the fourth and last step is the controlled return stroke mentioned under 4, in which the servo pump 7 is again operated by the control device 50 via the inverter 55, but in the reverse conveying direction as in the freewheel, with the buffered energy being reused by the converter 55 becomes.
  • the servo pump 7 pumps hydraulic medium M via the line 37 from the medium reservoir 5 into the lower cylinder chamber 32 and increases the pressure there.
  • the valve 4 is opened again.
  • the working piston 2 and the plunger 10 is thereby lifted back by means of the servo pump 7 back into the starting position or in another starting position.
  • Through the open valve 4 thereby displaced hydraulic medium M flows from the rear cylinder chamber 31 in the medium storage fifth
  • the lower cylinder space 31 is a pressure transmitter 12 assigned to monitor and measure the pressure.
  • the signals of the pressure transmitter 12 are transmitted via a line 52 to the control device 50.
  • FIG. 1 and 2 is the pressure transmitter associated with a connecting line 38 between a drive cylinder space of the servo pump 17 and the rear cylinder chamber 31, while in the FIG. 3 and 4 the hydraulic line 37 is associated between the power steering pump 17 and the rear cylinder chamber 31.
  • the pressure transducer 12 measures the pressure for controlling or regulating the pressure, in particular for the working stroke.
  • the pressure transducer 14 measures the pressure at the front cylinder chamber 32 in particular for monitoring function, z. Example, whether the workpiece is in contact with the pressing tool or is not held up at all, which would be reflected in the distinction of the limit value for the pressure.
  • step 1 it is also possible to omit the idle stroke or freewheel in step 1, for example, only for a finishing stroke as a working stroke, in which then only the eccentric works, which z. B. occurs when stretching.
  • An advantage of the pressing machine and the pressing method according to the invention is that the working stroke or the upper working point of the lower working point of the working stroke are arbitrarily adjustable within the total stroke or maximum stroke and the overload can be worked at any point of the stroke secured by the pressure relief valves , Furthermore, no weight compensation of the plunger is required as in mechanical Exzeterpressen.
  • the drive via the eccentric unit delivers high torques at lower dead center or lower operating point with lower drive power than with hydraulic presses. There is no power-controlled hydraulic pump required. Furthermore, no flywheel is required and the eccentric can work only in a partial angle range.
  • the servo pump 6 serves in particular to compensate for leaks in the hydraulic system and can pump additional hydraulic medium into the hydraulic system from the medium reservoir 5.
  • the servo pumps 6, 7 and 17 are in particular hydraulic servo pumps, for example axial piston pumps, driven by position-controlled servomotors 61, 71 and 171, which hold the pump rotors or pistons, and equipped with a hydraulic compensation reservoir, in particular the medium reservoir 5.
  • the hydraulic medium M may be an oil or water or a mixture thereof or else a so-called HFA emulsion.
  • the compression volume is usually higher with oil than with water and can be, for example, around 2% by volume at 300 bar.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Presses (AREA)
  • Press Drives And Press Lines (AREA)

Claims (9)

  1. Presse destinée à presser des pièces et présentant
    a) au moins deux outils de presse et au moins un poussoir (10) sur lequel au moins l'un des outils de presse (15) est disposé et exécute pour presser les pièces des déplacements de travail auxquels est associée une course de travail dans laquelle au moins deux outils de presse sont déplacés l'un vers l'autre,
    b) au moins une unité hydraulique d'entraînement du poussoir prévue pour le poussoir et présentant au moins un corps de travail (2) déplacé ou déplaçable à l'aide d'une chambre de travail (3) remplie d'un fluide hydraulique, le corps de travail séparant l'une de l'autre une première partie (31) et une deuxième partie (32) de la chambre de travail, le poussoir (10) étant accouplé au corps de travail (2),
    c) au moins un dispositif (11) de mesure de la position du poussoir qui mesure directement ou indirectement la position du poussoir (10) au moins le long de la course de travail,
    d) au moins une réserve (5) de fluide qui conserve du fluide hydraulique,
    e) au moins un premier dispositif hydraulique de transport (170, 8, 9) raccordé hydrauliquement à la première partie (31) de la chambre de travail et de préférence également à la réserve (5) de fluide, et dont la direction de transport est réversible,
    f) au moins un deuxième dispositif (70) de transport hydraulique qui comporte une unité de transport d'une servo-pompe (7), qui est raccordé hydrauliquement d'une part à la deuxième partie (32) de la chambre de travail et d'autre par à la réserve (5) de fluide et dont la direction de transport est réversible,
    g) au moins une soupape hydraulique asservie (4) raccordée hydrauliquement entre la première partie (31) de la chambre de travail et la réserve (5) de fluide et pouvant commuter entre une position fermée et une position ouverte,
    h) un dispositif de contrôle (50) raccordé au dispositif (11) de mesure de la position du poussoir, coopérant avec le premier dispositif hydraulique de transport (170) et le deuxième dispositif hydraulique de transport (70) ainsi qu'avec la soupape hydraulique asservie (4) en contrôlant automatiquement, par commande du premier dispositif hydraulique de transport (170) et du deuxième dispositif hydraulique de transport (70) ainsi que de la soupape hydraulique asservie (4), les débits volumiques et les pressions ainsi que le sens d'écoulement du fluide hydraulique (M) entre la réserve (5) de fluide et la première partie (31) de la chambre de travail et entre la réserve (5) de fluide et la deuxième partie (32) de la chambre de travail en fonction de la position mesurée du poussoir, de déroulements conservés en mémoire ou souhaités du déplacement du poussoir (10) et/ou d'informations introduites par les utilisateurs, la presse étant caractérisée en ce que, par:
    i) un troisième dispositif de transfert hydraulique (60) qui comporte une unité de transport (60) d'une servo-pompe (6) raccordée hydrauliquement d'une part à la première partie (31) dans la chambre de travail et d'autre part à la réserve (5) de fluide, et dont la direction de transport est réversible.
  2. Presse selon la revendication 1, présentant au moins une des caractéristiques suivantes ou une combinaison quelconque de ces caractéristiques :
    a) la chambre de travail est configurée comme cylindre de travail (3),
    b) le corps de travail est configuré comme piston de travail (2),
    c) la première partie et la deuxième partie de la chambre de travail forment une partie supérieure et une partie inférieure de la chambre de travail,
    d) le corps de travail (2) est déplacé ou peut être déplacé verticalement et
    e) le poussoir (10) est accouplé au côté inférieur du piston de travail (2).
  3. Presse selon la revendication 1 ou la revendication 2, dans laquelle le premier dispositif de transport hydraulique comprend au moins un premier moteur électrique de transport (171) et le deuxième dispositif de transport hydraulique comprend au moins un deuxième moteur électrique de transport (71) et dans laquelle les moteurs de transport sont raccordés par des conducteurs électriques à un convertisseur (55) raccordé au dispositif de contrôle (50), la vitesse de rotation et d'autre part le couple de rotation ou la puissance électrique des moteurs de transport pouvant être commandés individuellement par le ou les convertisseurs.
  4. Presse selon la revendication 3, dans laquelle le convertisseur (55) présente un accumulateur d'énergie par lequel l'énergie électrique produite par au moins l'un des moteurs de transport fonctionnant en génératrice pendant une phase de traitement est conservée temporairement et est utilisée dans une phase de traitement suivante ou ultérieure pour permettre le fonctionnement en moteur d'au moins l'un des moteurs de transport et de préférence de l'autre moteur de transport de l'autre dispositif de transport, l'accumulateur d'énergie du convertisseur comportant en particulier au moins un condensateur prévu dans un circuit intermédiaire du convertisseur.
  5. Presse selon l'une des revendications précédentes, dans laquelle le premier dispositif hydraulique de transport (170) est raccordé hydrauliquement et directement, c'est-à-dire sans soupape ou étrangleur intermédiaire, à la première partie (31) de la chambre de travail et dans lequel le deuxième dispositif hydraulique de transport (70) est raccordé hydrauliquement de manière directe, c'est-à-dire sans soupape ou étrangleur intermédiaire à la deuxième partie (32) de la chambre de travail.
  6. Presse selon l'une des revendications précédentes, dans laquelle
    a) le premier dispositif hydraulique de transport comporte au moins un piston d'entraînement (81) adjacent à une chambre d'entraînement (82) remplie de fluide hydraulique et déplacé ou apte à être déplacé par rapport à la chambre d'entraînement pour augmenter ou diminuer son volume, la chambre d'entraînement (82) étant reliée hydrauliquement à la première partie (31) de la chambre de travail de l'unité d'entraînement de poussoir, et dans laquelle le premier dispositif hydraulique de transport comporte au moins une unité décentrée (9) qui présente au moins un excentrique (92) apte à tourner autour d'un axe de rotation (D) à l'intérieur d'une plage angulaire prédéterminée de rotation, et disposé de préférence sur un disque excentrique, et qui est relié par une liaison mécanique, en particulier au moins une bielle (98) au piston d'entraînement (81) et entraîne ce dernier dans son déplacement par rapport à la chambre d'entraînement, la plage angulaire de rotation de l'excentrique étant disposée en particulier dans une partie tournée vers le piston d'entraînement, ou
    b) dans laquelle le premier dispositif hydraulique de transport comporte une unité de transport (170) d'une servo-pompe (17).
  7. Presse selon l'une des revendications 1 à 6, dans laquelle le dispositif de contrôle (50) est conçu et configuré de telle sorte qu'un cycle de travail contrôlé au moyen du dispositif de contrôle (50) en tenant compte des valeurs de position définies au moyen du dispositif de mesure de position comporte une course de pressage, une opération de décompression et une course de retour contrôlé,
    a) le premier dispositif de transport transportant lors de la course de pressage le fluide (M) provenant de la réserve (5) de fluide dans la première partie (31) de la chambre pour y établir une pression hydraulique de pressage, la vanne (4) étant fermée et l'outil de pressage étant repoussé contre la pièce,
    b) dans une opération de décompression, la soupape est fermée et le premier dispositif de transport est débranché ou est branché à un faible couple de rotation,
    c) lors de la course de retour contrôlé, le deuxième dispositif de transport transporte le fluide hydraulique depuis la réserve (5) de fluide jusque dans la deuxième partie de la chambre et la soupape est de nouveau ouverte de telle sorte que le corps de travail et le poussoir soient ramenés dans la position initiale ou également dans une autre position initiale, le fluide hydraulique refoulé à travers la soupape (4) ouverte s'écoulant depuis la deuxième partie de la chambre jusque dans la réserve de fluide.
  8. Presse selon la revendication 7, dans laquelle le dispositif de contrôle (50) est par ailleurs conçu et configuré de telle sorte que le cycle de travail comporte de plus une course libre avant la course de pressage, et dans laquelle
    a) lors de la course libre, le corps de travail (2) se déplace vers le bas dans la chambre de travail (3) sous l'action de la gravité, la soupape (4) étant ouverte au moins en partie par le dispositif de contrôle (50) et le deuxième dispositif de transport (7) commandé par le dispositif de contrôle (50) refoule le fluide (M) hors de la deuxième partie (32) de la chambre jusque dans la réserve (5) de fluide et/ou
    b) lors de la course libre, l'écoulement volumique de transport ou la pression de transport du deuxième dispositif de transport et/ou l'ouverture de la soupape (4) sont commandés de telle sorte que le déplacement du corps de travail (2) soit freiné ou accéléré selon une évolution prédéterminée du déplacement, le corps de travail se déplaçant jusqu'à un point de départ qui est en particulier un point auquel un outil de pressage entre en contact avec la pièce, ce qui est détecté ou surveillé en particulier par le dispositif de contrôle (50) qui mesure le chemin parcouru au moyen du dispositif (11) de mesure de position et/ou
    c) lors de la course libre, le premier dispositif de transport reste à l'arrêt, la soupape (4) est ouverte et le deuxième dispositif de transport est en service.
  9. Presse selon la revendication 7 ou la revendication 8, dans laquelle le dispositif de contrôle (50) est en outre conçu et configuré de telle sorte que lors de la course de pressage, le deuxième dispositif de transport produit en fonctionnant comme génératrice de l'énergie électrique qui est conservée temporairement dans l'accumulateur d'énergie du convertisseur et qui, et est réutilisée lors de la course de retour contrôlé qui suit, et/ou dans lequel, lors de l'opération de décompression, le premier dispositif de transport fonctionne en génératrice et produit de l'énergie électrique qui est conservée dans l'accumulateur d'énergie du convertisseur et est réutilisée par le deuxième dispositif de transport lors de la course de retour contrôlé.
EP12702817.3A 2011-02-02 2012-02-02 Presse de pressage de pièces Active EP2670586B1 (fr)

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DE102011000473.4A DE102011000473B4 (de) 2011-02-02 2011-02-02 Pressmaschine und Verfahren zum Pressen von Werkstücken
PCT/EP2012/051789 WO2012104384A1 (fr) 2011-02-02 2012-02-02 Presse et procédé de pressage de pièces

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US9889621B2 (en) 2018-02-13
CN103459134A (zh) 2013-12-18
EP2670586A1 (fr) 2013-12-11
CA2826250A1 (fr) 2012-08-09
US20140318390A1 (en) 2014-10-30
DE102011000473B4 (de) 2017-07-13
RU2013139676A (ru) 2015-03-10
CN103459134B (zh) 2016-08-17
WO2012104384A1 (fr) 2012-08-09
DK2670586T3 (en) 2018-08-13
CA2826250C (fr) 2017-08-15
ES2682065T3 (es) 2018-09-18
RU2601726C2 (ru) 2016-11-10
DE102011000473A1 (de) 2012-08-02

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