EP2036711B1 - Dispositif d'entraînement pour une presse plieuse - Google Patents

Dispositif d'entraînement pour une presse plieuse Download PDF

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Publication number
EP2036711B1
EP2036711B1 EP08005440.6A EP08005440A EP2036711B1 EP 2036711 B1 EP2036711 B1 EP 2036711B1 EP 08005440 A EP08005440 A EP 08005440A EP 2036711 B1 EP2036711 B1 EP 2036711B1
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EP
European Patent Office
Prior art keywords
pressure
drive device
press
line
piston
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
EP08005440.6A
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German (de)
English (en)
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EP2036711A1 (fr
Inventor
Markus Resch
Rudolf Scheidl
Peter Ladner
Karl Ladner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Trumpf Maschinen Austria GmbH and Co KG
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Trumpf Maschinen Austria GmbH and Co KG
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Publication of EP2036711A1 publication Critical patent/EP2036711A1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/163—Control arrangements for fluid-driven presses for accumulator-driven presses
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to a drive device, as described in the preamble of claim 1.
  • JP 2002-147404 A is a drive device for a bending press with a press frame, and with a fixed press beam and a relatively adjustable press beam known, the drive means of a hydraulic system with a hydraulic pump and a ring line with control valves for a switchable flow circuit for a pressure medium for alternately pressurizing two pressure chambers at least a pressure cylinder for the adjustment of the press bar.
  • the hydraulic system is an open, supplied with the pressure medium from a tank system, which excludes a pressure accumulator, since the different filling volumes of the pressure chambers of the hydraulic cylinder required equalization volume of the medium is conveyed into or out of the tank. This requires a correspondingly high total volume and delivery volume of the pressure medium for alternately pressurizing the hydraulic cylinder.
  • the rapid control comprises an additional control valve which establishes the connection between a pressure source, for example a pump, an accumulator, a press cylinder and the main control valve, via a connecting line. Furthermore, it comprises a bypass line which leads directly from the pressure source to the main control valve, which has a smaller cross-section than the connecting line running via the additional control valve and, if appropriate, also a throttle valve can be provided in this bypass line.
  • a pressure source for example a pump, an accumulator, a press cylinder and the main control valve
  • a bypass line which leads directly from the pressure source to the main control valve, which has a smaller cross-section than the connecting line running via the additional control valve and, if appropriate, also a throttle valve can be provided in this bypass line.
  • a hydraulic drive device for a press brake and a method for operating such is known, according to which in an open hydraulic system for feeding working cylinders, a hydraulic pump with a variable speed motor is operated.
  • the speed is variable depending on the movement processes, such as rapid traverse, press gear, emergency stop, return stroke, different requirements from a standstill up to a maximum speed controllable.
  • a hydraulic drive device in open design, with a tank, pump and supply line for acting on a pressure chamber of a working cylinder with a pressure medium is known.
  • a derivation of the pressure medium from the further pressure chamber can optionally be fed via a switching valve to the supply line or, depending on a defined pressure level in the supply line or the pressure chamber, can be returned to the tank via a discharge line.
  • Such an admixing of the outflowing pressure medium into the supply line results in an increase in the adjustment speed of the press beam before the actual pressing process, ie an express delivery and thus a shortened cycle time, for a given delivery rate of the pump.
  • the hydraulic drive device comprises a container for the pressure medium, which by means of an electric motor driven pump in a delivery circuit and control valves to the working cylinder, optionally the separate pressure chambers for a movement of a piston connected to the piston or a piston rod press ram for performing an adjustment for a press stroke and a return stroke is supplied.
  • a Nachsaug effet with a Nachsaugventil for rapid compensation of the volume flows of a different receiving volume having pressure chambers is provided between lines for the alternating admission of the pressure chambers of the working cylinder.
  • a hydraulic drive unit for a press for example, die-bending press, for actuating a press bar by means of a double-acting hydraulic cylinder with different effective surfaces
  • the hydraulic drive unit comprises a reservoir for a pressure medium, an electric motor driven pump and supply lines and control valves and a flow-connected, rechargeable pressure accumulator by means of which to compensate for the dead weight of the press bar a counter force is caused by the working cylinder.
  • Different piston active surfaces are basically known in hydraulic drives and, for example, in GB 749,571 A beschich.
  • the object of the invention is to provide a drive device for a bending press, with a high efficiency and thus energy-saving operation is achieved and the one compact, modular design allows.
  • the accumulator for a small storage volume of about a differential volume of the pressure chambers of the printing cylinder can be designed and dimensioned sufficiently, for example, with 0, 75-1 and this at an approximately required memory pressure of about 3 bar to 5 bar a complex memory safety block and a memory test can be omitted, and already at a small delivery volume of pressure medium and thus already at low pump performance very high rapid traverse speeds can be achieved.
  • cavitation in the impression cylinder is effectively avoided by the cartridge valve provided in the bypass line and designed for a high volume flow.
  • a press brake 2 operated by means of hydraulic drive device 1, in a simplified representation with a press frame 3, consisting essentially of side uprights 4, 5, a cross-dressing 6 and a fixed, aligned in a footprint 7 vertical plane 8 aligned plate-shaped press table 9 shown.
  • an upper press bar 11 is mounted adjustably guided in linear guides 10 on the side stand 4. 5, which in the illustrated embodiment of two pressure cylinders 12 as drive means 13 of the hydraulic drive device 1 according to - double arrow 14 - between an upper end position and a lower controllable end position, for applying a forming force to a between bending tools 15 of the press table 9 and press bar 11 for a forming process introduced workpiece, eg a sheet metal blank, sheet metal part etc.
  • the arrangement of the printing cylinder 12 is in the illustrated embodiment for a tensile force application during the forming process on the workpiece part of the press bar 11 and a pressure force application designed at a reversal of movement or a stop or holding the press bar 11 wherein the power transmission via a housing bearing and a rod bearing 17 takes place.
  • FIG. 2 is shown in detail the hydraulic drive device 1 for the press bar 11 using the example of a pressure cylinder 12 and a possible hydraulic system 18 in a simplified embodiment.
  • the pressure cylinder 12 For a reversible force application of the pressure cylinder 12 is designed as a so-called double-acting differential cylinder 19, with a cylinder housing 20 and therein adjustable by pressurization with a pressure medium, a cylinder chamber 21 in pressure chambers 22, 23 dividing piston 24th
  • the piston 24 is mounted on a piston rod 25 projecting from the cylinder housing 20 on one side and which is drive-connected in a protruding end region 26 to the press beam 11, e.g. by means of a bolt 27, which allows a tolerance of angular deviation.
  • the pressure cylinder 12 is attached according to the embodiment shown on a side surface 28 of the side stand 5, wherein the piston rod 25 protrudes from the cylinder housing 20 in a pressure-sealed rod feedthrough 29 of an end flange 30 facing away from the footprint 7 and as previously described in the end portion 26 is drivingly connected to the press bar 11 by means of the bolt 27.
  • the pressure cylinder 12 is supported by the piston rod 25 of the press beam 11 in the rest against the action of a deadweight component - according to arrow 31 -, ie that the piston rod 25 is exposed in this operating condition of a compressive stress, the pressure load in addition to the own weight component - According to arrow 31 - by acceleration forces by the movement of the press bar 11 - according to double arrow 14 - both during braking as well as a reversal of motion varies and this is to be considered in the dimensioning of the piston rod 25.
  • the pressure chambers 22,23 are 25 different piston active surfaces 32, 33 facing through the unilaterally led out from the cylinder chamber 21 piston, wherein the rod-side Kolbenwirk Structure 32 forms a circular ring surface of a circular surface with an inner diameter 34 of the cylinder chamber 21 minus a circular area of a piston rod diameter 35 and the opposite to the piston 24 opposite piston effective surface 33 of a circular area with the inner diameter 34 of the cylinder chamber 21 corresponds.
  • a ratio of the piston effective areas 32, 33 is greater than 1 to less than 1.5, which is equivalent to the different volume flows for acting on the pressure chambers 22, 33 from the hydraulic system 18 to perform a work cycle, which comprises twice the adjustment path between an upper and lower end position of the press bar.
  • the hydraulic system 18 can now also be seen in a simplified form in the form of a hydraulic scheme for controlling the hydraulic cylinder 12, which is a closed and essentially tankless hydraulic system 18.
  • the pressure cylinder 12 is supplied from the hydraulic system 18 with the pressure medium via a pressure line 36 in the piston-side pressure chamber 23 for the opening movement and via a pressure line 37 in the rod-side pressure chamber 22 for the closing movement.
  • the pressure line 36 connects the pressure chamber 23 with a port 38 of a control valve 39 and the pressure line 37, the pressure chamber 22 with a port 40 of another control valve 41st
  • Connections 42, 43 of the control valves 39, 41 are fluidly connected to a ring line 44 in which a via a speed and Dreu exercisessregelbaren drive motor 45, in particular an electric motor 46, operated hydraulic pump 47 is arranged whereby a medium flow according to - arrows 48, 49 - corresponding to a selected Direction of rotation according to - double arrow 50 - of the drive motor 45 and thus the hydraulic pump 47 optionally between the control valves 39, 41 can be reversed.
  • the ring line 44 forms a first line strand 51 between a first port 52 of the hydraulic pump 47 and the port 42 of the control valve 39 and a second line strand 53 between a second port 54 of the hydraulic pump 47 and the port 43 of the control valve 41, wherein according to the selected direction of rotation of the electric motor 46 and a first or second switching position of the control valves 39, 41 is a flow connection between the hydraulic pump 47 and the piston-side pressure chamber 23 or the rod-side pressure chamber 22 of the pressure cylinder 12, or the flow connection between the ring line 44 and the pressure line 36 for the piston-side pressure chamber 23, or between the ring line 44 and the pressure line 37 for the rod-side pressure chamber 22 of the pressure cylinder 12, is interrupted.
  • a bypass line 55 branches off, which leads to a second connection 56 of the control valve 41.
  • the ring line 44 is fluidly connected to a pressure accumulator 57 via a 3/2-way control valve 58 of which a port 59 of the control valve 58 via a line 60 to the wiring harness 51 and another port 61 of the control valve 58 via a line 62 to the wiring harness 53rd is connected and the pressure accumulator 57 is connected to a port 63 of the control valve 58.
  • This flow connection of the pressure accumulator 57 by means of the lines 60, 62 in conjunction with corresponding switching positions of the control valve 58 allows a need-based storage or release of a proportion of the circulating pressure medium whereby short control operations are achieved and the required amount of pressure medium in the hydraulic system 18 is kept low.
  • control valves 39, 41, 58 are in the illustrated embodiment Zweiwolfs- electrical switching valves, preferably piston valves with spring return and are in the following Description of the function of each operating state different switch positions, with reference to cross-reference to the representation in the figures, with the letters (A) for a first switching position and (B) for a second switching position.
  • This displacement volume can be absorbed by a very small pressure accumulator 57, or hydraulic accumulator.
  • the required pressure in this pressure accumulator 57 - he also exercises the hold function in the operation - is for a typical embodiment at 2 bar to 8 bar, preferably 3 bar to 5 bar and is of a storage volume of 0.5 1 to 2.5 1, preferably 0.75 to 1.0 1 go out. This provides the basis for getting along with no pressure storage block and no special memory check according to the pressure vessel guidelines.
  • the accumulator 57 performs two functions, such as hold function and tank function (pre-charged tank) for storing and dispensing a differential volume of the pressure medium due to the pressure chamber 22 retracting piston rod 24, or in the case of a both sides projecting piston rod - as explained in more detail later - the difference in volume of the two rod elements.
  • hold function and tank function pre-charged tank
  • the pressure cylinder 12 is a differential cylinder with a relatively small surface area of the piston rod 25.
  • the piston rod 25 is directed upward and suitably drivingly connected to the press beam 11 and supports it or pulls it down during a forming process.
  • the working pressure of the medium acts in the rod-side pressure chamber 22, ie, on the annular surface of the piston 24. Since in the case of a Maschinenteilumformung the piston rod 25 is claimed to train, there is no risk of buckling. Compressive stress exists only by the proportionate weight of the press bar 11 while holding the press bar 11 and in addition by an acceleration component when stopping or during the movement of the press bar upwards.
  • the lower pressure chamber 23 has a larger effective area than the upper, a controlled lowering or holding up of the press bar 11 in the rapid traverse circuit is possible.
  • the pressure cylinder 12 corresponds to a pure plunger cylinder with the surface of the piston rod 25 as a hydraulic active surface. Only an upwardly directed plunger can compensate for a downwardly directed weight force.
  • the hydraulic pump 47 is in principle a hydraulic four-quadrant machine.
  • the main stress under pressure occurs during the working process, ie when the work piece is re-shaped, so that it can be designed as a one-sided pump operated in the other quadrants at substantially lower pressures.
  • variable speed electric motor 46 With the variable speed electric motor 46, the speed and positioning of the press bar 11 is controlled. He works in both directions to the press bar 11 to move up and down.
  • the control valve 39 is a 2/2-way valve and serves to hold up the press bar 11 and to realize an emergency stop, wherein it is switched to position (A).
  • the control valve 41 is a 3/2-way valve and is used for rapid traverse operation. In the operation it is in position (A), in rapid traverse in position (B).
  • the control valve 58 is a 3/2-way valve and also serves the rapid traverse operation switching. In the operation it is in position (B), in rapid traverse in position (A).
  • the pressure accumulator 57 is a low-pressure accumulator with a relatively small volume. With his pressure he holds the press bar 11 in the operation over the effective surface of the piston 24 against the weight of the press bar 11 high. In rapid traverse downwards, it absorbs the volume of oil displaced by the piston rod 25 when the pressure cylinder 12 retracts. He acts as a tank in this phase.
  • Fig. 2 illustrated hydraulic drive device 1, broken down into the phases of a typical Abkantreaes, ie, starting from an upper rest position of the press bar 11 in a lower dead center position and subsequent upward movement in the rest position.
  • the control valves 39, 41 switch to the state (B), the control valve 58 switches to the state (A), whereby the connection 54 of the hydraulic pump 47 is connected to the pressure accumulator 57.
  • the electric motor 46 and thus the hydraulic pump 47 are rotated, the press bar 11 moves down.
  • about 90% of the volume displaced from the piston-side pressure chamber 23 is received by the rod-side pressure chamber 22.
  • the corresponding oil flow flows via the bypass line 55 and the control valve 41.
  • the oil flow delivered by the hydraulic pump 47 into the pressure accumulator 57 corresponds to the displaced relatively small rod volume relative to the ring side volume, therefore a very high rapid traverse speed is achieved.
  • the control valve 41 switches to the positions (A), while the control valve 58 switches to state (B) whereby the line 51 is connected to the pressure accumulator 57.
  • the hydraulic pump 47 conveys into the rod-side pressure chamber 22 and obtains a large force over the annular surface of the pressure cylinder 12.
  • the applied pressure from the accumulator 57 pressure in the piston-side pressure chamber 23 keeps the press bar 11 high even if no pressing forces acting on the press bar 11.
  • control valves 39,41 and the control valve 58 remain in the same positions as in the case of operation down. However, the electric motor 46 and the hydraulic pump 47 rotate in the other direction.
  • the medium pressure in the accumulator 57 raises the press bar 11 high, the engine speed controls the lifting speed whereby a controlled decompression is possible, ie reduction of reaction forces by spring force of the workpiece, Deformation of the deformation occurring during bending of the press bar 11 and the press frame 3, in particular the side stand.
  • the switching positions of the control valves 399 41, 58 are as in the case of rapid down but upon reversal of the conveying direction of the hydraulic pump 47.
  • the hydraulic pump 47 presses over the differential surface is equal to the piston rod surface the piston 24 and thus the press bar 11 upwards.
  • the control valve 39 is in the switching position (A) whereby the press bar is held by the medium pressure in the pressure chamber 23.
  • the hold-up and emergency stop controlled by the control valve 39, provides a cost-effective solution, e.g., as compared to mechanical brakes acting on the electric motor 46 or the press beam 11, e.g. by the application of a cost-effective, powered by a frequency converter asynchronous motor as an electric motor 46th
  • FIG. 3 another embodiment of the hydraulic control device with a preferred variant of the pressure cylinder 12 as a differential cylinder 19 of the press brake 2 and the hydraulic system 18 is shown.
  • the pressure cylinder 12, in the illustrated embodiment, for example, stationary relative to the press table 9, has a continuous piston rod 25, with a projecting upwards in the direction of the press bar 11, the cylinder housing 20 rod member 64 and a in the direction of the footprint 7, the cylinder housing 20 by projecting rod member 65.
  • the press beam 11 is drivingly connected to the rod member 64.
  • the rod member 65 is to achieve a predetermined area ratio on the piston 24 of the pressure chamber 23 for raising the press beam 11 facing annular surface 66 and the pressure chamber 22 for the operation facing pressure surface 67.
  • a rod diameter 68 of the rod member 64 is greater than a rod diameter 69 of the rod member 65, whereby the annular surface 66 is larger than the annular surface 67 and wherein the area ratio is in a preferred embodiment, approximately greater than 1 to less than 1.5.
  • the application of the downwardly led rod member 65 ensures a preferred area ratio to comply even with a required larger rod diameter 68, to avoid too high buckling load by a high weight of the press bar 11 and high acceleration forces.
  • the hydraulic system 18 provides for the control valve 39 and control valve 41 a plurality of control and regulating elements 70 and control lines 71, as described in detail later.
  • control valves 39, 41 By means of the control valves 39, 41, relatively high volume flows flow at rapid traverse which produce appreciable pressure losses on directly actuated industrial switching valves of nominal size 6. As a result, cavitation in the upper pressure chamber 22 would occur in any case during rapid traverse downwards. Therefore, hydraulically pilot operated valves are preferably used, which allow such flow rates at acceptable pressure drops. In the case of the control valve 41, this is a pilot-operated cartridge valve 72 and, in the case of the control valve 39, a pilot operated, non-returnable check valve 73. If the pilot stage is designed to be redundant, the functions provided for the control valve 39 are emergency redundant and redundant.
  • control valve 41 is a 2/2-way valve and the control valve 58 is a 4/2-way valve.
  • the hydraulic pump 47 delivers the corresponding oil volume of the retracting rod element 64 minus the volume of the extending rod element 65, ie a differential volume via the control valve 58 into the pressure accumulator 57.
  • the remaining oil volume flows via the bypass line 55 and the pressure line 37 into the pressure chamber 22 the printing cylinder 12th
  • the throttle valve 76 is provided in the leading from the wiring harness 51, bypassing the hydraulic pump 47 to the control valve 58 line 77.
  • a decompression phase in which a controlled relaxation of the pressing force occurred deformations of the press bar 11 and the press frame, in particular the side stand as well as degradation of the return spring force of the workpiece is initiated
  • the wiring of the control valves 39, 41 and the control valve 58 is the same as in the operating state “down” but with a reversal of the direction of rotation of the drive motor 45 and the hydraulic pump 47, whereby the flow of the hydraulic pump 47 against the conveying direction for the "operation - downwards "is reversed.
  • the hydraulic pump 47 conveys the oil volume corresponding to the extending rod element 64 from the pressure accumulator 57 via the line branch 51 into the pressure chamber 23 of the pressure cylinder 12.
  • the oil volume displaced from the pressure chamber 22 is discharged directly via the control valves 41 and 39 located in this switching state Pressure chamber 23 fed, whereby the funded by the hydraulic pump 47 oil volume is relatively small.
  • Fig. 7 is the hydraulic system 18 for the operating state "emergency stop" of the press bar 11 during a rapid traverse movement down - shown in accordance with arrow 80 - with the corresponding switching positions of the control valves 39, 41 and the control valve 58.
  • Fig. 8 and 9 is another embodiment of the drive device 1 for the opposite of the fixed press table 9 adjustable press bar 11, with the different design hydraulic systems 18, as already detailed in the Fig. 2 and 3 are shown.
  • the differential cylinder 19 is secured immovably to the press frame 3, in particular to the cylinder housing 20, on the side stand 4 and has the continuous piston rod 25, which is formed from the rod elements 64, 65 provided with different diameters.
  • the arrangement is chosen so that exerted on the piston rod 25 on the adjustable press beam 11 in an adjustment of the press bar 11 in the direction of the press table 9 - according to arrow 31 - a compressive force or a dependent on the weight of the press bar 11 supporting force.
  • the press bar 11 in the rod bearing 17 With the press bar 11 in the rod bearing 17, the smaller rod diameter 68 having rod member 64 is coupled.
  • control valves 39, 41, 58 The wiring of the control valves 39, 41, 58 is shown for the operating state "standstill of the press bar 11" as on the one hand for holding the press bar 11 in one upper death position or an intermediate position z.
  • B. is provided an Eilstopp.
  • Fig. 10 and 11 is another arrangement of the pressure cylinder 12 of the drive device 1 and the previously described differently designed hydraulic systems 18, which is therefore not discussed in detail shown.
  • the pressure cylinder 12 has in this embodiment, the one-sided protruding piston rod 25 and is e.g. connected immovably to the housing 20 and the housing bearing with the adjustable press beam 11.
  • the projecting piston rod 25 is coupled immovably in a firmly connected to the press table 9 or the press frame 3 abutment 85. This results in an adjustment of the press bar 11 in the direction of the press table 9 - according to arrow 31 - a tensile load in the piston rod 25 or a pressure load by a conditional by the weight of the press table 11-force when holding the press table 11 in an upper dead or intermediate layer plus a force such as occurs during braking of the press bar 11 in an emergency stop, as also already described in the preceding figures.
  • the drive device 1 is shown with a further variant of the hydraulic system 18.
  • the pressure cylinder 12 has the one-sided protruding piston rod 25.
  • a tensile load acts in the piston rod 25 during a pressing operation.
  • the hydraulic system 18 has the ring line 44 with the line strands 51, 53.
  • the wiring harness 51 connects the hydraulic pump 47 with the pressure chamber 23 for acting on the piston effective surface 33.
  • the wiring harness 53 connects the hydraulic pump 47 with the pressure chamber 22 with the piston ring surface 32nd
  • the pressure accumulator 57 is selectively activated or deactivated via a line 83 and a control valve 84 to the wiring harness 51, or via a line 85 and a control valve 86 to the wiring harness 53, and switching positions of the control valves 84 according to the respective operating state.
  • a control valve 87, 88 is arranged in each case.
  • a further control valve 89 is arranged in the bypass line 55, which connects the wiring harness 51 with the wiring harness 53.
  • the hydraulic pump is designed for direction-reversible conveying and is operated with the variable-speed drive motor 45.
  • control valves 84, 86, 87, 88, 89 18 2/2-way valves are provided according to this variant of the hydraulic system.
  • FIG. 13 the switching states for the operating states "rapid traverse downward" and “rapid traverse upward” are shown.
  • the pressure chambers 22, 23 of the pressure cylinder 12 via the bypass line 55 and the control valves connected to passage 87, 89 conductively connected, whereby a small volume flow corresponding to the Differenzvolumcn the pressure chambers 22, 23, from the also connected to the passage Control valve 86 and line 85 is conveyed depending on the direction of movement of the press bar 11 in the pressure accumulator 57 or fed from this into the ring line 44.
  • bypass line 55 with the control valve 89 is locked in this operating state, as well as the line 85 between the wiring harness 53 and the pressure accumulator 57 by the locking position of the control valve 86th

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

Claims (19)

  1. Dispositif d'entraînement (1) pour une presse plieuse, avec un bâti de presse (3) avec une table de presse (9) et des pressoirs (11) pouvant être déplacés par rapport à la table de presse (9) par l'intermédiaire d'un système hydraulique (18) comprenant une pompe hydraulique (47), avec un moteur d'entraînement (45) réglable, des moyens de commutation et de commande et des conduites de pression et un accumulateur de pression (57) avec des cylindres de pression (12) alimentés par un fluide sous pression, et en ce que le système hydraulique (18) forme, avec une conduite annulaire (44) comprenant la pompe hydraulique (47), un circuit d'écoulement pouvant être contrôlé par des soupapes de commande (39, 41, 58, 84, 86, 87, 88, 89) pour le fluide sous pression avec une première portion de conduite (51) de la conduite annulaire (44) entre une chambre de pression (23) d'au moins un cylindre de pression (12) et de la pompe hydraulique (47) et avec une deuxième portion de conduite (53) de la conduite annulaire (44) entre une autre chambre de pression (22) du cylindre de pression (12) et de la pompe hydraulique (47) et l'accumulateur de pression (57) est relié en écoulement, par l'intermédiaire d'au moins une des soupapes de commande (58, 84, 86), au choix, avec la première portion de conduite (51) ou la deuxième portion de conduite (53) de la conduite annulaire (44) pour le logement ou la distribution d'un volume d'accumulation du fluide sous pression, caractérisé en ce qu'une surface d'action de piston (32) de référence, pour l'application de la force de pression sur les pressoirs (11), d'un piston (24) séparant une chambre de cylindre (21) dans les chambres de pression (22, 23) est inférieure à une surface d'action de piston (33) opposée et un rapport de surface entre les surfaces d'action du piston (32, 33) est de plus de 1 à moins de 1,5 et les portions de conduites (51, 53) sont reliées en écoulement aux chambres de pression (22, 23) du cylindre de pression (12) au moyen de combinaisons de soupapes hydrauliques adaptées directement par l'intermédiaire d'une conduite de bypass (55).
  2. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que l'accumulateur de pression (57) est reliée, par l'intermédiaire d'une conduite (83) et de la soupape de commande (84), avec la portion de conduite (51) de la conduite annulaire (44) et par l'intermédiaire d'une conduite (85) et de la soupape de commande (86) avec la portion de conduite (53) de la conduite annulaire (44).
  3. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que le cylindre de pression (12) est conçu avec une tige de piston (24) dépassant d'un côté.
  4. Dispositif d'entraînement selon la revendication 3, caractérisé en ce qu'une surface de section transversale de la tige de piston (25) représente 1/5 à 1/20 de la surface d'action du piston (32) entourant la tige de piston (24).
  5. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que le cylindre de pression (12) est conçu des éléments de tiges (64, 65) dépassant des deux côtés.
  6. Dispositif d'entraînement selon la revendication 5, caractérisé en ce que les diamètres (68, 69) des éléments de tiges (64, 65) sont différents, le diamètre (68) de l'élément de tige (64) reliés en entraînement avec le pressoir (11) mobile étant supérieur au diamètre (69) de l'autre élément de tige (65).
  7. Dispositif d'entraînement selon la revendication 5, caractérisé en ce que les diamètres (68, 69) des éléments de tiges (64, 65) sont différents, le diamètre (68) de l'élément de tige (64) reliés en entraînement avec le pressoir (11) mobile étant inférieur au diamètre (69) de l'autre élément de tige (65).
  8. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que, dans la conduite de bypass (55) se trouve une soupape à cartouche (72) pilotée hydrauliquement.
  9. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que la pompe hydraulique (47) et un moteur d'entraînement (45) de la pompe hydraulique (47) sont conçus pour un refoulement bidirectionnel du fluide sous pression.
  10. Dispositif d'entraînement selon la revendication 9, caractérisé en ce que le moteur d'entraînement (45) pour la pompe hydraulique (47) est constitué d'un moteur électrique (46).
  11. Dispositif d'entraînement selon la revendication 10, caractérisé en ce qu'une alimentation du moteur électrique (46) en énergie a lieu par l'intermédiaire d'un organe de régulation de la vitesse de rotation.
  12. Dispositif d'entraînement selon la revendication 11, caractérisé en ce que l'organe de régulation de la vitesse de rotation est constitué d'un convertisseur de fréquence.
  13. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que l'accumulateur d'énergie (57) est constitué d'un accumulateur basse pression, par exemple d'un accumulateur à vessie, d'un accumulateur à membrane, d'un accumulateur à pistons.
  14. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que la tige de piston (25) est reliée par l'intermédiaire d'un palier de tige (17) avec un pressoir mobile (11).
  15. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que la tige de piston (25) est reliée par l'intermédiaire d'un contre-palier (82) avec le bâti de presse (3).
  16. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que la tige de piston (25) est reliée avec la table de presse (9).
  17. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que le cylindre de pression (12) est fixé au bâti de presse (3) par l'intermédiaire d'un palier à boîtier (16).
  18. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que le cylindre de pression (12) est fixé au montant latéral (4, 5).
  19. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que le cylindre de pression (12) est fixé au pressoir (11) par l'intermédiaire d'un palier à boîtier (16).
EP08005440.6A 2007-09-12 2008-03-22 Dispositif d'entraînement pour une presse plieuse Active EP2036711B1 (fr)

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DE102021123910A1 (de) 2021-09-15 2023-03-16 HMS - Hybrid Motion Solutions GmbH Hydraulisches Antriebssystem mit einer 4Q Pumpeneinheit

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CN101835601B (zh) 2013-06-26
US20100212521A1 (en) 2010-08-26
AT505724A1 (de) 2009-03-15
WO2009033199A1 (fr) 2009-03-19
US8342086B2 (en) 2013-01-01
CN101835601A (zh) 2010-09-15
EP2036711A1 (fr) 2009-03-18
AT505724B1 (de) 2010-06-15

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