EP2335840A2 - Entraînement de presse hydraulique - Google Patents

Entraînement de presse hydraulique Download PDF

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Publication number
EP2335840A2
EP2335840A2 EP10015501A EP10015501A EP2335840A2 EP 2335840 A2 EP2335840 A2 EP 2335840A2 EP 10015501 A EP10015501 A EP 10015501A EP 10015501 A EP10015501 A EP 10015501A EP 2335840 A2 EP2335840 A2 EP 2335840A2
Authority
EP
European Patent Office
Prior art keywords
pressure
counter
hydraulic
holding
hydraulic machine
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
EP10015501A
Other languages
German (de)
English (en)
Other versions
EP2335840A3 (fr
EP2335840B1 (fr
Inventor
Marek Chmiel
Oliver Schneider
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2335840A2 publication Critical patent/EP2335840A2/fr
Publication of EP2335840A3 publication Critical patent/EP2335840A3/fr
Application granted granted Critical
Publication of EP2335840B1 publication Critical patent/EP2335840B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B30B15/16—Control arrangements for fluid-driven presses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/10—Devices controlling or operating blank holders independently, or in conjunction with dies
    • B21D24/14—Devices controlling or operating blank holders independently, or in conjunction with dies pneumatically or hydraulically
    • 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

Definitions

  • the invention relates to a hydraulic press drive a press for forming a held on a tool part workpiece, said tool part by means of a drive with respect to another tool part is movable.
  • the basic structure of such a sheet-metal forming press is for example from the DE 43 09 641 A1 or the DE 103 36 279 A1 known.
  • the forming of the sheet takes place by means of a tool whose upper tool part is movable via a mechanical or hydraulic main drive.
  • the sheet to be formed is supported on a blank holder of the lower tool part.
  • the lower tool part supported on a die cushion is accelerated with the sheet holder by means of a hydraulic drive to the travel speed of the upper tool part, so that the mechanical loads during closing of the tool are minimal.
  • both tool parts move at about the same speed, wherein a counter-holding force is applied to the lower tool part via a counter-holding cylinder.
  • the two tool parts are controlled so that the tool opens and the formed workpiece can be removed.
  • the adjusting according to the above embodiments motion profiles of the tool parts are, for example, in FIG. 2 of the DE 103 36 279 A1 shown.
  • the pressure medium flowing out of the counter-holding pressure medium is fed to a hydraulic machine during the controlled lowering of the die cushion, so that the hydraulic energy can be utilized to drive further consumers.
  • a disadvantage of these solutions is that accelerating and countering takes place via components arranged in a common hydraulic circuit, the acceleration frequently also taking place via a counter-holding cylinder, so that in the case of the above-described recirculation during counter-holding, the adequate pressure medium supply of the other components must also be taken into account and compromises are required in the control of the feedback.
  • the present invention seeks to provide a hydraulic press drive, in which the efficiency of the conversion of hydraulic energy during recovery is improved.
  • the hydraulic press drive has a workpiece holding tool part which is movable by means of at least one rapid traverse cylinder for accelerating and which can be acted upon by means of a counter holding cylinder with a holding force, the counter holding cylinder and the rapid traverse cylinder each having its own hydraulic circuit is associated with a hydraulic machine for supplying pressure medium ,
  • the pressure medium supply with regard to the optimized conversion of the hydraulic energy to drive the hydraulic machines can be largely controlled independently.
  • the utilization of the hydraulic energy of the outflowing from the or the counter-holding pressure fluid can be optimized independently of the control of the rapid traverse cylinder, so that an energy efficient operation of the press is ensured.
  • an effective counter-pressure chamber of the counter-holding cylinder via a pilot-operated check valve is connected to the tank in order to reduce the counter-holding pressure or to switch quickly between rapid traverse and counter hold.
  • this check valve is pre-controlled, so that a fast switching can be ensured.
  • a hydraulic accumulator arrangement is provided in the pressure line between the pressure chamber of the counter-holding cylinder, which acts in the counter-holding direction, and the associated hydraulic machine, which is charged in the regenerative mode.
  • This memory arrangement may be associated with a memory switching valve arrangement, with a fast-switching memory switching valve which opens in a passage position, a pressure medium connection between the counter-pressure effective pressure chamber and the tank and shuts off in a blocking position, this pressure medium connection in the direction of the tank.
  • a plurality of parallel-connected check valves are arranged, which allow a large pressure medium flow rate for charging the hydraulic accumulator assembly.
  • the rapid traction drive is executed in a variant of the invention with a plurality of parallel hydraulic machine units, which are preferably mechanically coupled to each other, so that the pressure medium supply of the rapid traction cylinder arrangement over several small, inexpensive and good responsive units takes place.
  • these units are designed with reversible delivery / discharge direction or the pressure medium supply direction via a directional control valve arrangement.
  • the rapid traverse cylinder assembly is designed with at least one differential cylinder with different active surfaces, wherein the smaller effective surface with the pressure port of the hydraulic machine assembly of the rapid traction drive and the larger effective surface via the latter directional control valve with this pressure port or tank is connectable. In this way, the travel direction of the rapid traverse cylinder arrangement can be adjusted in a simple manner by switching the directional control valve.
  • the effort for the realization of the hydraulic machines can be minimized if, in the regenerative mode, the hydromachine associated with the counter-holding drive drives a hydraulic machine associated with the rapid traverse drive.
  • the hydraulic machine assigned to the counter-holding drive has a constant-displacement motor which drives a variable-displacement pump, via which in turn an adjusting motor of the hydraulic machine is driven in rapid traverse, which in turn drives a variable-displacement pump for supplying pressure to the rapid-traction cylinder arrangement.
  • a directional control valve can be arranged in the pressure medium flow path between the two adjusting motors, is tapped via the pressure medium for supplying pressure medium further consumer.
  • the invention can be used particularly advantageously if the press drive is designed with a control device, via which the storage switching valve and / or the pilot-operated check valve when a pressure threshold in the counter-holding direction is exceeded effective pressure chamber of the counter-holding cylinder assembly is switched to feedback.
  • This switching can be continuous or pulsed.
  • Such a press has a two-part tool in which the workpiece to be deformed is formed.
  • An in FIG. 1 not shown upper part of the tool is designed as a die.
  • the press has a mechanical or hydraulic main drive to drive a pull ram carrying the upper tool part.
  • the other, lower tool part usually forms a male part, also called a press ram, which dips into the female mold when the tool is closed.
  • the thereby formed workpiece is fixed in position via a sheet holder.
  • This and the punch (male) are also mounted movable in the vertical direction on a press table.
  • the workpiece lower part (punch, male) is supported on a hydraulic die cushion 1, the hydraulic drive in FIG. 1 is shown.
  • This hydraulic drive consists in principle of a rapid traction drive 2 and a counter-holding drive 4, which are each arranged in a separate hydraulic circuit.
  • the die cushion drive is designed as a two-circuit system, wherein the control of the components lying in each circle can be largely independent of the control of the components located in the other circle, so that in particular the above-explained recovery of hydraulic energy when countering with high Efficiency can be performed - but this will be explained in more detail below.
  • the counter-holding drive 4 has a counter-holding cylinder 6 acting on the die cushion 1 with a plunger 8, which has a large diameter in comparison to a rapid-action cylinder 10 described below.
  • FIG. 1 shows by way of example a counter-holding cylinder 6 and a rapid traverse cylinder 10 - of course, the die cushion drive can also be designed with a plurality of counter-holding or rapid traverse cylinders.
  • the counter-holding cylinder 6 has a pressure chamber 12 which is delimited by the plunger 8 and which decreases when the die cushion 1 or the lower tool part is lowered. This lowering is effected by the very high weight of the lower tool part and the die cushion 1.
  • the lifting to the upper tool part is effected by pressure medium supply into the pressure chamber 12 and by controlled shut-off of this pressure chamber 12 with respect to a tank T.
  • the pressure chamber 12 is via a pilot-operated check valve fourteenth and a tank line 16 connected to this tank T. As shown in FIG. 1 allows this check valve 14 a suction of pressure medium from the tank T during extension of the counter-holding cylinder. 6
  • the pilot-operated check valve 14 is designed as a pilot operated valve and has a pilot valve 18, which is designed as a 3/2-way switching valve and the working port A is guided to a control port of the check valve 14.
  • a tank connection T is connected via a tank control line 20 to the tank T and an input connection P to a pressure control line 22.
  • the pilot valve 18 is designed as a quick-switching seat valve, so that a lekagetransport shut-off of the respective control line sections is possible.
  • a spring-biased basic position b of the tank T is shut off and the working port A connected to the pressure port P.
  • the pilot valve 18 can be switched to a switching position in which the output terminal A is connected to the tank port T. In this switching position a, the valve 14 acts as a normal check valve.
  • the check valve 14 is unlocked, so that pressure fluid from the pressure chamber 12 to the tank T can flow.
  • the pressure chamber 12 is further connected via a pressure line 24 to a hydraulic accumulator assembly 26, which consists for example of one or a plurality of series-connected hydraulic accumulators, in the illustrated embodiment of five hydraulic accumulators.
  • the pressure line 24 opens downstream of the hydraulic accumulator 26 in a working line 28 which leads to the tank T and in which a counter-holding hydraulic machine 30 is arranged, which can operate both as a pump and as a motor.
  • the hydraulic machine 30 is designed with a variable speed motor 32 which drives either the hydraulic machine 30 (pump) or is driven by this (hydraulic motor).
  • the hydraulic machine 30 is driven, so that via the motor 32 according to another consumer can be supplied with energy.
  • the hydraulic accumulator assembly 26 is also charged.
  • the counter hold pressure is determined during recovery, inter alia via the counter hold hydraulic machine 30.
  • the check valve assembly 34 is part of a in FIG. 1 indicated memory switching valve assembly 36, which in addition to the one or more check valves 34 has a memory switching valve 38, which is designed as a fast-switching 2/2-way valve.
  • This storage switching valve 38 is arranged in a branching off from the pressure line 24 relief line 40, which opens into the tank T.
  • spring-biased home position b of the memory switching valve 38 this pressure medium connection to the tank T out, so that the pressure fluid can flow even with locked check valve 14 from the pressure chamber 12 to the tank T out.
  • This storage switching valve 38 is also designed as a lekagetransports seat valve. In principle, one could also in such a construction on the unlockable check valve 14 renounce, since the pressure medium connection of the tank 12 can also be switched via the memory switching valve 38.
  • a fuse block 42 for the memory device 26 is provided in the pressure line 24.
  • This hedging block 42 has a pressure limiting valve 44 and a switching valve 46 connected in parallel therewith, by means of which a pressure medium connection of the pressure line 24 to a tank line 50 can be opened when a storage pressure which is detected, for example, via a sensor 48 is exceeded.
  • the hedge block 42 further has a manual valve 48 for manually opening this pressure medium connection.
  • the rapid traverse cylinder 10 is executed in the illustrated embodiment as a synchronous cylinder with a Gleichgangkolben 52 which limits two annular spaces 54 and 56 with the same active surfaces.
  • the two annular spaces 54, 56 are each connected via a working line 58 or 60 to a hydraulic machine arrangement 62.
  • This hydraulic machine arrangement 62 has in the illustrated embodiment a plurality - more precisely, three hydraulic machines 62a, 62b, 62c, which can work both as a pump and as a hydraulic motor and the conveying / swallowing direction is reversible.
  • each of the hydraulic machines is designed with a variable-speed drive motor 64 which drives the respective hydraulic machine in the pump mode and is driven in the engine mode.
  • variable-speed drive it is also possible to use a hydraulic machine which can be pivoted over 0, for example an axial piston machine or a large number of such axial piston machines.
  • limiting pressure relief valve 66 and a pressure in the working line 58 limiting pressure relief valve 68 are arranged in pressure medium connections between the two working lines 58, 60.
  • a 2/2-float valve 70 is arranged in a bypass line 72 connecting the two working lines 58, 60.
  • This float valve 70 is biased to a closed position b and can be switched electrically and / or hydraulically in a switching position a, in which the two working lines 58, 60 are directly connected to each other, so that the rapid traverse cylinder 10 is operated in a floating position, in which the pressure medium is displaced almost without loss between the two annular spaces 54, 56.
  • the two working lines 58, 60 are each connected via a check valve 74, 76 to a feed line 78, which is connected via a further check valve 80 to a pressure port of a feed pump 82.
  • the pressure in the feed line 78 is limited by a feed pressure relief valve 84.
  • a further hedging block 86 is provided, wherein the pressure in this area can be detected by a pressure transducer 88.
  • the hedging block 86 has, in principle, the same structure as the hedging block 42.
  • a feed hydrogen reservoir 90 which can be connected to the feed line 78 or the two working lines 58, 60 by opening a manual valve 92.
  • the rapid traverse circuit 2 is designed as a closed hydraulic circuit, depending on the conveying direction of the hydraulic machine assembly 62 pressure medium from one of the annular spaces 54, 56 withdrawn and in the other pressure chamber 56, 54 can be promoted to the rapid traverse cylinder 10 upwards (in Direction of the upper tool part, not shown) or to move down. Due to the small compared to the counter-holding cylinder 6 effective area of the rapid traverse cylinder 10 and the high capacity of the hydraulic machines, the die cushion 1 can be accelerated very quickly. It is possible to control the individual hydraulic machines 62a, 62b, 62c individually, together or in any desired combination. In principle, it is also possible to carry out hydraulic machines with different delivery / displacement volumes.
  • the hydraulic machines 62 can also be operated in the engine mode, wherein, for example, in the case of a lowering of the die cushion 1 caused by the high own weight, the pressure medium flows out of the decreasing annular space 56 via the hydraulic machine arrangement 62 to the other, increasing pressure chamber 54 and then accordingly the hydraulic machines 62 are driven and drive accordingly the drive motors 64, so that this energy can be used to drive other components.
  • a sheet is placed on the blank holder, not shown, which is aligned with respect to the highest point of the male.
  • the upper tool part (die) has moved over the main drive to its top dead center.
  • the die cushion 1 is in the region of its top dead center, but the two tool parts are spaced from each other.
  • this top dead center of the pressure chamber 12 has its maximum volume, being sucked via the pilot-operated check valve 14 and / or located in the switching position a storage valve 38 pressure fluid from the tank T in the pressure chamber 12 during extension of the counter-holding cylinder 6.
  • the upper die part (die) is then moved downwards.
  • the die cushion 1 is accelerated downward by corresponding activation of the hydraulic machine arrangement 62 - accordingly, pressure medium is sucked out of the annular space 56 of the rapid traverse cylinder 10 and conveyed into the annular space 54.
  • the die cushion 1 is accelerated such that when closing the tool, the relative speed between the two tool parts (die, male) is very low or equal to 0, so that the closing process is relatively gentle and no impact and thus damage to the sheet holder or the tool or the press components is to be feared.
  • the check valve 14 and / or the memory switching valve 38 is unlocked or controlled, so that the pressure medium substantially lossless from the decreasing pressure chamber 12 is pushed out to the tank T.
  • the pressure fluid connection of the pressure chamber 12 is controlled to the tank T, so that builds up a counter-holding pressure in the pressure chamber 12, which can be adjusted by appropriate control of the pilot valve 18 and the counter-holding hydraulic machine 30 with a predetermined profile.
  • the switching between rapid traverse and counter-holdings can be controlled essentially via the pilot valve 18, in which case the memory switching valve 38 remains in its illustrated blocking position a.
  • the pressure medium flowing out of the pressure chamber 12 via the pressure line 24 while it is being counter-charged loads the hydraulic accumulator assembly 26 into its memory position valve 38 located in its switching position a and flows via the counter-holding hydraulic machine 30 to the tank T, so that it drives the motor 32 and this energy can be used to drive other consumers.
  • the check valve assembly 34 ensures a sufficient flow cross-section, so that a comparatively large pressure medium volume flow can flow.
  • the storage switching valve 38 is switched to its passage circuit b (home position), so that the pressure medium from the pressure chamber 12 in bypassing the storage device 26 and the counter-holding hydromachine 30 flows toward the tank T.
  • the storage switching valve 38 is designed as a fast-switching valve, so that the switching can be done intermittently very quickly and also at high frequency and the desired counter-pressure profile is adjustable.
  • FIG. 2 shows an embodiment of the invention, in which the hydraulic machine 30 arranged in the counter-holding circuit 4 drives the hydraulic machine 62 of the rapid-action circuit 2.
  • the counterhold circuit 4 of the embodiment according to FIG. 2 has substantially the same structure as the counterhold circuit 4 of the basis FIG. 1 explained embodiment, so that only the differing components are explained and the rest of the above statements can be referenced.
  • FIG. 1 shows an embodiment of the invention, in which the hydraulic machine 30 arranged in the counter-holding circuit 4 drives the hydraulic machine 62 of the rapid-action circuit 2.
  • the pressure in the pressure chamber 12 is detected by a pressure transducer 98 and reported to the controller.
  • the arrangement of the pilot-operated check valve 14 with the pilot valve 18, the storage switching valve 38, the check valve assembly 34 and the hydraulic accumulator assembly 26 corresponds to that of the above-described embodiment, so that further explanations are unnecessary.
  • One difference is that the storage switching valve 38 is acted upon in the direction of its basic position b next to the spring also by the pressure in the pressure control line 22.
  • the counter-holding hydraulic machine 30 is - as already explained - connected to the executed by a single variable displacement pump 62 hydraulic machine assembly 62, the terminal P is connected via a pressure channel 100 with the two working lines 58 and 60, which open together in this embodiment in the pressure channel 100 , This pressure channel 100 branches off between the counter-holding hydraulic machine 30 and the check valve 118 from the pressure line 120.
  • a directional control valve 102 is arranged in the working line 60, which leads to the annular space 56 with a larger effective area, which is designed as a 3/3-way valve, which is designed to be electrically and / or hydraulically adjustable.
  • the hydraulic control of the directional control valve 102 via control ports y, x, wherein the control port y is connected via a control line 104 to the tank T and the control port x via a pressure control line 106 to the pressure channel 100.
  • a control oil filter 108 is provided in the pressure control line 106.
  • a rapid traverse storage arrangement 110 is furthermore provided in the pressure channel 100.
  • this connects the working lines 58, 60 with a float position line 112, which opens into the tank T, wherein in the working line 60 and in the floating position line 112 each have a damping throttle 114, 116 is provided.
  • the working line 60 is connected to the annulus 56 so that in both annular spaces 56, 54 the same pressure, i. the pressure in the pressure channel 100 is applied. Due to the area difference, the rapid traverse cylinder then moves upwards.
  • the annular space 56 is connected with larger effective area on the float position line 112 to the tank - since the other annulus 54 is always acted upon by the pressure in the pressure channel 100, the rapid traverse cylinder 10, but then either the check valve 14 or the storage valve 38 must be unlocked or switched to its open position, so that the pressure medium - as explained above - can be ejected from the pressure chamber 12 substantially without losses and no counter-pressure is built up.
  • the respective shift position of the directional valve 102 is detected and reported to the control of the press.
  • the Schmidthydromaschine 30 and running as a variable displacement hydraulic machine 62 are both connected to the motor 32, which is driven depending on the load situation or else drives the hydraulic machine 62 and the counter-holding hydraulic machine 30.
  • the pilot operated check valve 14 is opened via the pilot valve 18 (alternatively, the accumulator switching valve 38 can be opened) and the directional control valve 102 is moved to its switching position b, in which the annular space 56 is depressurized, so that the counter-retaining piston 94 and thus the Drawing cushion is accelerated in the direction of movement of the upper tool part (die).
  • the directional valve 102 is switched to its floating position (basic position) and the counter-pressure in the pressure chamber 12 controlled by appropriate control of the storage valve 38 and / or the pilot operated check valve 14 and thereby upon reaching a predetermined, energetically favorable for the return pressure range in the pressure chamber 12 switched so that the hydraulic accumulator assembly 26 is charged and the pressure fluid flows through the counterhold hydraulic machine 30 to the tank T and thereby drives the hydraulic machine 62 to charge the memory 110 over the annular spaces 54, 56 can be acted upon by a constant pressure, depending on the circuit of the directional control valve 102.
  • FIG. 3 shows a variant of the embodiment according to FIG. 2 , wherein the representation of the individual components is simplified.
  • the counterhold circuit 4 essentially corresponds to the embodiment described above, wherein the counter-holding cylinder 6 and the rapid traverse cylinder 10 are designed as in the embodiment described above, ie the counter-holding cylinder 6 is designed as a plunger cylinder with a plunger 8 and the rapid traverse cylinder 10 as a synchronous cylinder with a Gleichgangkolben 52, whose annular space 54 delimiting piston rod is connected to the plunger cylinder 8 or bears against this.
  • the pressure chamber 12 of the synchronous cylinder 6 can be connected to the tank T via the unlockable check valve 14.
  • This check valve 14 may - as in the embodiments described above - be provided with a pilot control.
  • the check valve assembly 34 and the accumulator valve assembly 36 are arranged.
  • the pressure medium flows during the return via the designed as a pump with two flow directions counter-holding hydraulic machine 30 and in the direction of the tank T opening check valve 118 to the tank T out.
  • the pressure line 24 can be connected to the tank T via the storage switching valve 38 when the storage arrangement 36 and the counter hold hydraulic machine 30 are bypassed.
  • the counter-holding hydraulic machine 30 is mechanically coupled to an adjustable hydraulic machine 120, which is designed in the illustrated embodiment as a pump with two flow directions. Furthermore, the motor 32, which can be driven via the hydraulic motor 30 or else drives the hydraulic motor and / or the pump 120, is located on the same axis.
  • a pressure port P of the adjustable hydraulic machine 120 is - similar to the embodiment described above - connected to the pressure channel 100, in which in turn a rapid traverse storage arrangement 110 is arranged with three hydraulic accumulators in this embodiment.
  • the pressure channel 100 leads in this embodiment to the pressure port P of an adjustable hydraulic motor 124, via which a variable displacement pump is drivable, which corresponds in the function of the hydraulic machine assembly 62 and therefore also provided with the same reference numerals.
  • the drive motor 64 On the same axis is the drive motor 64, which can either be driven by the hydraulic motor 122 or drives the machines 122, 62.
  • the two connections of the hydraulic machine 62 are connected to the working line 58 or 60 as in the previously described embodiments, so that depending on the conveying direction of the hydraulic machine 62 pressure medium to the annular space 54 or the annular space 56 is promoted and in a corresponding manner from the other pressure chamber is encouraged.
  • the other connection of the hydraulic motor 122 which is designed with two displacement flow directions, is connected to the tank T via a discharge channel 124.
  • adjustable hydraulic machines 120, 122, 62 may be designed in any desired manner, for example as axial piston machines with adjustable pivoting angle.
  • FIG. 3 branches from the pressure channel 100 from a supply line 124, which is guided to the pressure port P of a continuously adjustable consumer valve 126.
  • a tank connection T of this consumer valve 128 is connected to the tank T via a tank channel 130.
  • Two working ports A, B are connected via working channels 132, 134 with connections of a hydraulic consumer, not shown.
  • the ports A, B, P and T are connected together in a floating position.
  • the working port B is connected to the pressure port P.
  • the pressure medium connection between the pressure port P and the working port A is opened and adjusted in accordance with the working port B to the tank port T when adjusting in the direction b. In this way, it is possible to supply a further consumer with pressure medium via the variable displacement pump 120 driven by the counter-holding hydraulic machine 30 and the storage arrangement 110.
  • the operation of the embodiment according to Fig. 3 corresponds to that of the embodiment FIG. 2 ,
  • the pilot-operated check valve 14 and / or the storage switching valve 38 is opened, so that the pressure chamber 12 is connected to the tank T and the pressure medium can be ejected from the pressure chamber 12.
  • the over 0 pivotable variable displacement pump 62 is adjusted so that pressure medium is conveyed into the annular space 54 and removed from the annular space 56. Accordingly, the die cushion is accelerated by means of the rapid traverse cylinder 10.
  • the regeneration mode can be switched continuously at a certain pressure threshold in the pressure chamber 12 or in the form of a pulse modulation in order to ensure optimum energy conversion.
  • a hydraulic press drive with a rapid traverse cylinder and a counter-holding cylinder, which are each arranged in a separate hydraulic circuit with a hydraulic machine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Press Drives And Press Lines (AREA)
EP10015501.9A 2009-12-15 2010-12-10 Entraînement de presse hydraulique Not-in-force EP2335840B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009058407A DE102009058407A1 (de) 2009-12-15 2009-12-15 Hydraulischer Pressenantrieb

Publications (3)

Publication Number Publication Date
EP2335840A2 true EP2335840A2 (fr) 2011-06-22
EP2335840A3 EP2335840A3 (fr) 2014-12-31
EP2335840B1 EP2335840B1 (fr) 2021-02-17

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Application Number Title Priority Date Filing Date
EP10015501.9A Not-in-force EP2335840B1 (fr) 2009-12-15 2010-12-10 Entraînement de presse hydraulique

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EP (1) EP2335840B1 (fr)
DE (1) DE102009058407A1 (fr)
ES (1) ES2865726T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2384834A3 (fr) * 2010-05-03 2015-10-21 Schuler Pressen GmbH & Co. KG Vérin hydraulique pour un coussin de serre-flan hydraulique

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013007148B4 (de) 2013-04-25 2025-08-21 Robert Bosch Gmbh Hydraulischer Pressantrieb mit Energierückspeisung
EP3115190B1 (fr) 2015-07-06 2020-11-18 Feintool International Holding AG Dispositif et procede de commande de l'entrainement principal d'une presse pour decoupage de precision
DE102018120001A1 (de) * 2018-08-16 2020-02-20 Moog Italiana S.R.L. Digitales Pumpenachsensteuerungssystem

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4309641A1 (de) 1992-03-27 1993-09-30 Rexroth Mannesmann Gmbh Hydraulischer Antrieb für eine Presse, insbesondere für eine Blechformpresse
DE10336279A1 (de) 2003-08-07 2005-03-03 Bosch Rexroth Ag Einrichtung zur Steuerung des Ziehvorgangs bei einer Transferpresse

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0074421B1 (fr) * 1981-09-12 1985-05-22 L. SCHULER GmbH Agencement d'emboutissage pour presses à poinçon d'emboutissage actionné mécaniquement
DE4218914A1 (de) * 1992-06-10 1993-12-16 Erfurt Umformtechnik Gmbh Hydraulische Zieheinrichtung in einer Presse

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4309641A1 (de) 1992-03-27 1993-09-30 Rexroth Mannesmann Gmbh Hydraulischer Antrieb für eine Presse, insbesondere für eine Blechformpresse
DE10336279A1 (de) 2003-08-07 2005-03-03 Bosch Rexroth Ag Einrichtung zur Steuerung des Ziehvorgangs bei einer Transferpresse

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"Handbuch der Umformtechnik", 1996, SPRINGER VERLAG

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2384834A3 (fr) * 2010-05-03 2015-10-21 Schuler Pressen GmbH & Co. KG Vérin hydraulique pour un coussin de serre-flan hydraulique

Also Published As

Publication number Publication date
ES2865726T3 (es) 2021-10-15
EP2335840A3 (fr) 2014-12-31
DE102009058407A1 (de) 2011-06-16
EP2335840B1 (fr) 2021-02-17

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