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EP3272511B1 - Dispositif d'entraînement hydraulique - Google Patents

Dispositif d'entraînement hydraulique Download PDF

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Publication number
EP3272511B1
EP3272511B1 EP17181834.7A EP17181834A EP3272511B1 EP 3272511 B1 EP3272511 B1 EP 3272511B1 EP 17181834 A EP17181834 A EP 17181834A EP 3272511 B1 EP3272511 B1 EP 3272511B1
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EP
European Patent Office
Prior art keywords
hydraulic
press
piston chamber
drive device
hydraulic drive
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
EP17181834.7A
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German (de)
English (en)
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EP3272511A1 (fr
Inventor
Roland Menzel
Martin Rossi
Max Hälterlein
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.)
DORST Technologies GmbH and Co KG
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DORST Technologies GmbH and Co KG
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Publication of EP3272511A1 publication Critical patent/EP3272511A1/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
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure

Definitions

  • the invention relates to a hydraulic drive device with a press cylinder for a hydraulic press, preferably a powder press, as well as a hydraulic press, preferably a powder press and a method for pressing a pressed part, in particular for powder pressing a powder pressed part.
  • the present invention relates to a hydraulic press or a corresponding method and a corresponding drive device which are designed for a (maximum) pressing force of over 500 kN, in particular over 1000 kN, preferably over 1500 kN.
  • the central component of hydraulic presses are press cylinders that fulfill various functions.
  • press cylinders are used to open and close a press tool of the hydraulic press at high speed (rapid traverse).
  • a high force in the closing direction is built up via such press cylinders.
  • the high closing forces required for pressing require a correspondingly large piston area to generate a maximum pressing force at a predetermined maximum pressure.
  • With a large piston area correspondingly high volume flows result, so that pumps and valves of comparatively large construction or dimensions are required in the prior art.
  • the rapid traverse and press functions are separated in the prior art.
  • Such press cylinders can be equipped with an integrated or with a separate rapid traverse cylinder.
  • lock cylinder pistons are pulled along during the rapid traverse movement.
  • the supply of hydraulic fluid can be fed separately from a container ("suction operation”).
  • the piston and annulus can be cyclically connected by means of a hydraulic switching valve ("flushing").
  • a hydraulic drive device with a press cylinder for a hydraulic press, preferably a powder press, the hydraulic drive device being configured to feed a cylinder piston in a forward rapid traverse at increased speed to a press part and in a press traverse at low speed to press the pressed part
  • the press cylinder has a cylinder piston which defines a piston chamber and a rod chamber
  • a pump device is provided for providing a volume flow of a hydraulic fluid in the piston chamber so that the pressing chamber is passed through
  • a hydraulic storage device for providing at least of a part, in particular a predominant part, of a volume flow of the hydraulic fluid into the piston chamber, so that the forward rapid traverse is passed through without an additional rapid traverse cylinder to the R ealization of the rapid traverse is provided
  • the piston chamber and rod chamber being connected or connectable via a fluid connection
  • the pump device and the hydraulic storage device being arranged within this fluid connection, connected fluidically in parallel to one another, a first fluid connection section connected to the piston chamber
  • a central idea of the invention is to provide a hydraulic storage device and to configure the hydraulic drive device as a whole in such a way that at least a considerable (in particular predominant) part of the comparatively large volume flow that is required in forward rapid traverse is provided via this hydraulic storage device.
  • a "predominant part” is understood to mean a proportion of at least 50%. The proportion can, however, preferably also be at least 70% or more preferably at least 90%.
  • the hydraulic storage device is a device for storing the hydraulic fluid under pressure (for example to at least 10 bar or at least 30 bar or at least 35 bar). Furthermore, the hydraulic storage device can be discharged and thereby emit a volume flow of the hydraulic fluid.
  • the hydraulic storage device can in particular be a hydraulic storage device with a gas clamping device.
  • the hydraulic storage device can comprise a (pressure) container.
  • the hydraulic storage device can have a movable element (for example a movable piston) for separating hydraulic fluid and a (pressurized) gas. The hydraulic fluid can then be pressed into the hydraulic storage device (in particular the container) against the pressure of the gas.
  • the hydraulic storage device can be used to access an additional press cylinder to implement rapid traverse, as in the prior art, see for example DE 10 2011 116964 A1 , usually provided, can be omitted.
  • the drive device is considerably simplified in structural terms, as a result of which costs can be reduced.
  • the control, in particular regulation, of such a drive device is also simplified, since a second press cylinder (with correspondingly assigned elements, such as in particular a feed pump) can be dispensed with.
  • the hydraulic drive device according to the invention manages with only one pump device. Overall, the costs (both in terms of production and operation or maintenance) are significantly reduced.
  • (Hydraulic) oil is particularly suitable as the hydraulic fluid.
  • the hydraulic drive device is preferably configured to move the cylinder piston away from the pressing part in a reverse rapid traverse at increased speed, with a volumetric flow of hydraulic fluid emerging from the piston chamber in reverse rapid traverse being at least partially, in particular predominantly, transferred into the hydraulic storage device.
  • the hydraulic storage device is thus used at the same time as a receptacle for the (large) amount of hydraulic fluid that is pushed out of the piston chamber during rapid reverse traverse.
  • the hydraulic storage device is loaded again so that it can be unloaded again in a next cycle (in a subsequent forward rapid traverse). This further simplifies the structure and the control or regulation effort.
  • the speed in the forward rapid traverse and / or reverse rapid traverse can be at least 1.5 times, more preferably at least 3 times, even more preferably at least 4 times as high as the speed in the pressing step.
  • the entire volume flow flowing in reverse rapid traverse out of the piston chamber can (exclusively) be pushed in the direction of the hydraulic storage device and pump device.
  • the respective pressures in the piston chamber and rod chamber are preferably set in such a way that the forces acting on the piston are neutralized (at least substantially; there may be at least a small difference to overcome frictional forces or the like).
  • the press cylinder is preferably a differential cylinder.
  • a ratio of the larger area to the smaller area can preferably be at least 2, more preferably at least 5.
  • an upper limit value for the said ratio can be at most 20, more preferably at most 10.
  • a ratio of (approximately) 7 is particularly preferred. With such a dimensioning, the hydraulic drive device can be operated particularly effectively.
  • the hydraulic drive device is configured in such a way that, in a first force reduction phase, the piston chamber can be connected to the hydraulic storage device, preferably via the pump device, in such a way that the pressure in the piston chamber (from its maximum value) to the pressure level of the hydraulic Storage device is degradable.
  • the hydraulic drive device can be configured in such a way that a pressure in the rod space can be increased (preferably by the pump device) in a second force reduction phase.
  • the storage and pump devices are therefore used synergistically here in order to enable a controllable and reliable reduction in force. Damage to the part to be pressed (pressed part) can thus be prevented (or at least less likely).
  • the piston chamber and the rod chamber can be connected or connectable via a fluid connection.
  • the pump device and the hydraulic storage device (in particular connected in parallel fluidically to one another) can be arranged.
  • a first fluid connection section connected to the piston chamber can be connected to a first branch point (branch structure) from which a second fluid connection section branches off in the direction of the pump device and a third fluid connection section branches off in the direction of the hydraulic storage device.
  • a fourth fluid connection section connected to the rod space can be connected to a second branch point (branch structure) from which a fifth fluid connection section branches off in the direction of the pump device and a sixth fluid connection section branches off in the direction of the hydraulic storage device.
  • a first valve device is particularly preferably provided in the fifth fluid connection section.
  • a second valve device can be provided in the sixth fluid connection section.
  • a (non-return) valve is preferably connected fluidically in parallel to the second valve device.
  • the pump device can comprise a bidirectional pump, in particular a 4-quadrant pump, and / or a servomotor.
  • a bidirectional pump for example 1- or 2-quadrant pump
  • corresponding valves servo valves or the like
  • An effective area (i.e. an area that is defined by the cylinder piston and is in contact with the hydraulic fluid) of the piston chamber can be at least 200 cm 2 , preferably at least 450 cm 2 and / or at most 1100 cm 2 , preferably at most 700 cm 2 .
  • Lower and upper limit values for the effective area of the rod space can correspond to the upper values divided by 7.
  • a ratio of an effective area of the piston space to an effective area of the rod space can be at least 3, preferably at least 6 and / or at most 15, preferably at most 9. This ratio is particularly preferably (approximately) 7. With such a ratio, effective driving and control of the press cylinder can be made possible.
  • the hydraulic storage device can have a volume of at least 10 l, preferably at least 30 l and / or at most 100 l, preferably at most 70 l.
  • a volume of (approximately) 50 l is particularly preferred.
  • the volume occupied by the hydraulic fluid in the hydraulic storage device can be at least 3 l, preferably at least 10 l and / or at most 30 l, preferably at most 20 l. This volume is particularly preferably (approximately) 12 liters.
  • the hydraulic storage device can have a base pressure (ie a pressure without loading by the hydraulic fluid) of at least 10 bar, preferably at least 25 bar and / or at most 80 bar, preferably at most 50 bar. This pressure is particularly preferably 30 bar.
  • the pressure within the hydraulic storage device can be at least 12 bar, preferably at least 30 bar and / or at most 100 bar, preferably at most 60 bar. In this case, the pressure is particularly preferably (approximately) 40 bar.
  • the rod space preferably forms an annular space which is defined by an inner wall of the press cylinder and a rod running through the rod space.
  • a ratio between the inner diameter of the press cylinder and the outer diameter of the rod can, for example, be at least 1.05; preferably at least 1.15 and / or at most 1.5; preferably at most 1.3.
  • At least one control device in particular regulating device for controlling, in particular regulating, the individual components of the hydraulic drive device is provided.
  • Corresponding sensors can be assigned to this control device (regulating device), which, for example, provide a measured variable (pressure and / or volume flow) at a connection (outlet or input) of the piston chamber and / or a connection Measure (output or input) of the rod space. From the measured variables (in particular pressure and / or volume flow), necessary switching operations, in particular with regard to the first and second valve devices described above, can then be carried out and / or the pump device can be controlled (regulated) accordingly.
  • a hydraulic press preferably a powder press, comprising a hydraulic drive device of the type described above.
  • the above-mentioned object is achieved in particular by a method according to claim 11 for pressing a pressed part, in particular for powder pressing a powder pressed part, preferably using a hydraulic drive device of the type described above and / or a hydraulic press of the type described above, in particular a hydraulic powder press of the above described type, solved, wherein a cylinder piston of a press cylinder is guided in a forward rapid traverse at increased speed to a pressed part and the pressed part is pressed in a press cycle at low speed of the cylinder piston, wherein in the press cycle via a pump device, a volume flow into a piston chamber of the press cylinder is pumped, with at least a part, in particular a predominant part, of a volume flow being provided in the piston chamber in rapid traverse via a hydraulic accumulator device.
  • a volume flow is provided either by the pump device or the hydraulic accumulator device, this means in particular that the corresponding volume flow is guided directly into the piston chamber or rod chamber, at best via corresponding valve devices or is derived from there (i.e. in particular not via the respective other facility).
  • the provision of a volume flow via (or through) the hydraulic storage device should mean that the respective volume flow is not passed via the pump.
  • the provision of a volume flow by the pump device is intended to mean that the respective volume flow is not additionally conducted via the hydraulic storage device.
  • the cylinder piston can be moved away from the pressed part in a reverse rapid traverse at increased speed, wherein a volume flow emerging from the piston chamber in reverse rapid traverse can be transferred at least partially, in particular predominantly, into the hydraulic storage device.
  • a volume flow into the piston chamber is preferably made available in the forward rapid traverse partly from the rod chamber, in particular via the pump device.
  • the volume flow exiting the piston chamber is partially transferred into the rod chamber, in particular via the pump device, in reverse rapid traverse.
  • the piston chamber in a first force reduction phase, is connected to the hydraulic accumulator device, preferably via the pump device, in such a way that the pressure in the piston chamber is reduced to the pressure level of the hydraulic accumulator device.
  • a pressure in the rod space is increased, preferably by the pump device, in a second force reduction phase.
  • the drive device described above and the press described above can be configured accordingly in order to generate such a pressing force.
  • the drive device described above and the press described above can be configured accordingly in order to generate such a pressure.
  • a drive and a hydraulic control of a press cylinder of a hydraulic press are proposed in particular.
  • the press cylinder is preferably designed in a differential design (with a large piston area and a small differential area). This can result in comparatively high volume flows during the movement movements at a connection to the piston chamber, which can be supplied by a hydraulic storage device. Comparatively low volume flows can be present at a connection to the rod space, which are necessary for positioning the Cylinder piston can be regulated.
  • the control of the force or pressure, position and speed of the cylinder piston can take place by means of a pump unit (in particular a servo pump unit).
  • the design of the pump can enable 4-quadrant operation, so that pressures can be regulated in both flow directions.
  • the design of the drive device according to the invention results in a number of advantages.
  • an additional cylinder rapid traverse cylinder
  • it is a clamped system, so that efficiency is increased.
  • the present structure enables extremely precise (active) force reduction. No complex piping is necessary.
  • the size of the pump device can be comparatively small. It may be possible to dispense with further pump devices. Overall, there are cost savings in providing the (cylinder) drive, valves, pump and control.
  • Fig. 1 shows a press cylinder 1, which is used both for opening and closing a (not in Fig. 1 shown) pressing tool at a high speed (Rapid traverse) as well as to build up a high force in the closing direction at low speed (press traverse for pressing a pressed part).
  • the press cylinder has a differential design and has a comparatively large piston area A 1 for generating a (maximum) pressing force and a comparatively small differential area A 2 for the retraction of a cylinder piston 9. Because of this construction of the press cylinder 1, a comparatively high volume flow of hydraulic fluid has to be supplied to a connection 10 of the piston chamber.
  • This high volume flow Q 1 to the piston chamber is realized by a hydraulic accumulator device 4.
  • a connection 11 of a rod space 12 is regulated by a pump device 2. In this forward rapid traverse, a first valve device 3 (Y1) is open and a second valve device 5 (Y2) is closed.
  • the first and second valve devices 3, 5 are each closed.
  • the hydraulic fluid (oil supply) is then supplied to the piston chamber 13 (exclusively) via the pump device 2.
  • the pressure and (delivery) speed are regulated via the speed and torque of a servo motor 7 of the pump device 2.
  • the pump device 2 here comprises a bidirectional pump 14th
  • the force of the press cylinder is reduced in two phases.
  • a first force reduction phase the second valve device 5 opens, so that a connection between the hydraulic accumulator device 4 and the rod space 12 is established.
  • the pressure in the piston chamber 13 is reduced (from its maximum value) to the pressure level of the hydraulic accumulator device 4.
  • a compression volume is relieved from the piston chamber 13 via the pump device 2 into the hydraulic accumulator device 4.
  • the second force reduction phase begins.
  • the second valve device 5 is closed and the first valve device is opened.
  • the second force reduction phase a pressure build-up takes place in the rod space 12 (the pressure p 1 in the piston space remains at the value of the pressure in the hydraulic accumulator device 4).
  • a force on the cylinder piston is reduced proportionally to this pressure increase in the rod space 12 (down to zero).
  • the cylinder piston 9 starts an upward opening movement (without a transition).
  • the volume flow rate Q 1 from the piston chamber 13 is being pushed back into the hydraulic storage device 4 (for the most part), the volume flow portion corresponding to Q 2 is conveyed via the pump means. 2
  • Fig. 2 shows in addition to the representation according to Fig. 1 Arrows that indicate the respective volume flow (or a relief flow).
  • arrows 15 show a volume flow that results in forward rapid traverse.
  • Arrows 16 show a volume flow that results during the pressing phase.
  • Arrows 17 show a volume flow (relief flow) during the first force reduction phase.
  • Arrows 18 show a volume flow (relief flow) that results during the second force reduction phase.
  • Arrows 19 show a volume flow that results in reverse rapid traverse.
  • connection 10 of piston chamber 13 and connection 11 of rod chamber 12 are explained below.
  • a first fluid connection section 21 initially closes (see FIG Fig. 1 ), which is connected to a first branch point 31.
  • a second fluid connection section 22 branches off from the first branching point 13 in the direction of the pump device 2 and a third fluid connection section 23 in the direction of the hydraulic storage device 4.
  • the first valve device 3 is provided in the third fluid connection section.
  • the connection 11 of the rod space 12 is connected to a second branching point 32 via a fourth fluid connection section 24.
  • a fifth fluid connection section 25, which is connected to the pump device 2 branches off from there.
  • a sixth fluid connection section 26 branches off from there and is connected to the hydraulic storage device 4.
  • the second valve device 3 is located in the sixth fluid connection section 26.
  • a seventh fluid connection section 27, in which the check valve 6 is arranged, runs parallel to the second valve device 5. In the present context, it basically depends on how the individual elements are connected either in series or in parallel with one another. In general, however, both the pump device 2 and the hydraulic accumulator device 4 are arranged in a fluid connection between the piston chamber and the rod chamber.
  • the design of the drive device according to the invention results in a number of advantages.
  • an additional cylinder rapid traverse cylinder
  • it is a clamped system, so that efficiency is increased.
  • the present structure enables extremely precise (active) force reduction. No complex piping is necessary.
  • the size of the pump device can be comparatively small. It may be possible to dispense with further pump devices. Overall, there are cost savings in providing the (cylinder) drive, valves, pump and control.
  • a control device (not shown) is preferably also provided.
  • Sensors for example a pressure and / or volume flow measuring device
  • the control device switches the valves 3, 5 and controls the pump device 2 in such a way that the necessary volume flows and pressures are realized.
  • a force during pressing can be 1600 kN.
  • a force at the end of the first force reduction phase can amount to 320 kN.
  • a force at the end of the second force reduction phase can amount to 0 kN.

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

Claims (15)

  1. Installation d'entraînement hydraulique avec un cylindre de presse (1) pour une presse hydraulique, de préférence une presse à poudre, laquelle installation d'entraînement hydraulique est configurée pour guider un piston de cylindre (9) vers une pièce à presser dans une course en marche avant rapide à vitesse augmentée et presser la pièce à presser dans une course de pressage à petite vitesse,
    dans laquelle le piston de cylindre (9) définit un espace pour le piston (13) et un espace pour la tige (12),
    dans laquelle une installation de pompage (2) est prévue pour fournir un débit volumique d'un liquide hydraulique dans l'espace pour le piston (13) de sorte que la course de pressage est parcourue,
    dans laquelle une installation d'accumulation hydraulique (4) est prévue pour fournir au moins une partie, en particulier la majeure partie d'un débit volumique du liquide hydraulique dans l'espace pour le piston (13), de sorte que la course en marche avant rapide est parcourue, sans utiliser un cylindre de course rapide supplémentaire pour réaliser la course rapide, l'espace pour le piston (13) et l'espace pour la tige (12) communicant ou pouvant communiquer par une communication de fluide, l'installation de pompage (2) et l'installation d'accumulation hydraulique (4) étant disposées dans cette communication de fluide dans un montage hydraulique parallèle l'une à l'autre, une première section de communication hydraulique (21) en communication avec l'espace pour le piston communiquant avec un premier embranchement (31) à partir duquel une deuxième section de communication de fluide (22) bifurque en direction de l'installation de pompage (2) et une troisième section de communication de fluide (23) bifurque en direction de l'installation d'accumulation hydraulique (4),
    dans laquelle une quatrième section de communication de fluide (24) en communication avec l'espace pour la tige (12) communique avec un deuxième embranchement (32) à partir duquel une cinquième section de communication de fluide (25) bifurque en direction de l'installation de pompage (2) et une sixième section de communication de fluide (26) en direction de l'installation d'accumulation hydraulique (4).
  2. Installation d'entraînement hydraulique selon la revendication 1, caractérisée en ce que l'installation d'entraînement hydraulique est configurée pour éloigner le piston de cylindre (9) de la pièce à presser dans une course en marche arrière rapide à vitesse augmentée, un débit volumique du fluide hydraulique qui sort de l'espace pour le piston pendant la course en marche arrière rapide étant au moins partiellement, en particulier en majeure partie, transféré dans l'installation d'accumulation hydraulique (4).
  3. Installation d'entraînement hydraulique selon la revendication 1 ou 2, caractérisée en ce que l'installation d'entraînement hydraulique est configurée de telle sorte que pendant la course en marche avant rapide, un débit volumique soit fourni en partie dans l'espace pour le piston (13) à partir de l'espace pour la tige (12), en particulier par l'installation de pompage (2), et/ou
    dans laquelle l'installation d'entraînement hydraulique est configurée de telle manière que le débit volumique sortant de l'espace pour le piston (13) pendant la course en marche arrière rapide puisse être en partie transféré dans l'espace pour la tige (12), en particulier par l'installation de pompage (2).
  4. Installation d'entraînement hydraulique selon la revendication 1, 2 ou 3, caractérisée en ce que le cylindre de presse (1) est un cylindre différentiel,
    dans lequel le rapport entre la plus grande surface et la plus petite surface est de préférence d'au moins 2, mieux encore d'au moins 5, et/ou
    dans lequel un rapport entre la plus grande surface et la plus petite surface est de préférence de 20 au maximum, mieux encore de 10 au maximum.
  5. Installation d'entraînement hydraulique selon l'une des revendications précédentes, caractérisée en ce que l'installation d'entraînement hydraulique est configurée de telle sorte que, dans une première phase de constitution de la force, l'espace pour le piston (13) puisse être mis en communication avec l'installation d'accumulation hydraulique (4), de préférence par l'installation de pompage (2), de telle sorte que la pression dans l'espace pour le piston (13) puisse être constituée jusqu'au niveau de pression de l'installation d'accumulation hydraulique (4), et/ou
    dans laquelle l'installation d'entraînement hydraulique est configurée de telle manière que, dans une deuxième phase de constitution de la force, une pression dans l'espace pour la tige (12) puisse être augmentée, de préférence par l'installation de pompage (9).
  6. Installation d'entraînement hydraulique selon l'une des revendications précédentes, caractérisée en ce qu'une première installation de soupape (3) est prévue dans la troisième section de communication de fluide (23) et/ou dans laquelle une deuxième installation de soupape (5) est prévue dans la sixième section de communication de fluide (26), une soupape antiretour (6) étant en outre montée de préférence en parallèle à la deuxième installation de soupape (5) dans le circuit hydraulique.
  7. Installation d'entraînement hydraulique selon l'une des revendications précédentes, caractérisée en ce que l'installation de pompage (2) comprend une pompe bidirectionnelle (14), en particulier une pompe à quatre quadrants, et/ou un servomoteur (7).
  8. Installation d'entraînement hydraulique selon l'une des revendications précédentes, caractérisée en ce qu'une surface active de l'espace pour le piston (13) mesure au moins 200 cm2, de préférence au moins 450 cm2 et/ou au maximum 1100 cm2, de préférence au maximum 700 cm2 et/ou
    un rapport entre une aire active de l'espace pour le piston (13) et une aire active de l'espace pour la tige (12) est d'au moins 3, de préférence d'au moins 6 et/ou au maximum de 15, de préférence au maximum de 9, et/ou
    l'installation d'accumulation hydraulique (4) présente au volume d'au moins 10 l, de préférence d'au moins 30 l et/ou au maximum de 100 l, de préférence au maximum 70 l, et/ou
    l'installation d'accumulation hydraulique (4) présente une pression de base d'au moins 10 bars, de préférence d'au moins 25 bars et/ou au maximum de 80 bars, de préférence au maximum de 50 bars.
  9. Installation d'entraînement hydraulique selon l'une des revendications précédentes, caractérisée en ce qu'il est prévu au moins un dispositif de commande, en particulier un dispositif de régulation pour la commande, en particulier la régulation, des différents composants de l'installation d'entraînement hydraulique.
  10. Presse hydraulique, de préférence presse à poudre, comprenant une installation d'entraînement hydraulique selon l'une des revendications précédentes.
  11. Procédé pour le pressage d'une pièce pressée, en particulier pour le pressage de poudre pour obtenir une pièce en poudre pressée, utilisant une installation d'entraînement hydraulique selon l'une des revendications 1 à 9 et/ou une presse, en particulier une presse à poudre, selon la revendication 10, dans lequel un piston de cylindre (4) d'un cylindre de presse est guidé dans une course en marche avant rapide à vitesse augmentée vers une pièce à presser et la pièce à presser est pressée en une course de pressage à basse vitesse du piston de cylindre (9),
    dans lequel, pendant la course de pressage, une installation de pompage (2) pompe un débit volumique en direction d'un espace pour le piston (13) du cylindre de presse (1), une installation d'accumulation hydraulique (4) fournissant au moins une partie, en particulier la majeure partie, d'un débit volumique dans l'espace pour le piston (13) pendant la course à marche rapide.
  12. Procédé selon la revendication 11, caractérisé en ce que le piston de cylindre est éloigné de la pièce à presser dans une course en marche arrière rapide à vitesse augmentée, un débit volumique du fluide hydraulique qui sort de l'espace pour le piston pendant la course en marche arrière rapide étant au moins partiellement, en particulier en majeure partie, transféré dans l'installation d'accumulation hydraulique (4).
  13. Procédé selon la revendication 11 ou 12, caractérisé en ce que pendant la course en marche avant rapide, un débit volumique est fourni en partie dans l'espace pour le piston (13) à partir de l'espace pour la tige (12), en particulier par l'installation de pompage (2), et/ou
    pendant la course en marche arrière rapide, le débit volumique du fluide hydraulique sortant de l'espace pour le piston est partiellement transféré dans l'espace pour la tige, en particulier par l'installation de pompage,
    et/ou dans une première phase de constitution de la force, l'espace pour le piston (13) est mis en communication avec l'installation d'accumulation hydraulique (4), de préférence par l'installation de pompage (1), de telle façon que la pression dans l'espace pour le piston (13) soit réduite au niveau de pression de l'installation d'accumulation hydraulique (4) et/ou
    dans une deuxième phase de constitution de la force, une pression est augmentée dans l'espace pour la tige (12), de préférence par l'installation de pompage (2).
  14. Procédé selon l'une des revendications 11 à 13, caractérisée en ce qu'une force de pression d'au moins 100 kN, de préférence d'au moins 500 kN, de préférence encore de 1500 kN est créée et/ou
    une pression différentielle maximale d'au moins 100 bars, de préférence d'au moins 250 bars, est créée entre l'espace pour le piston (13) et l'espace pour la tige (12).
  15. Utilisation d'une installation d'entraînement hydraulique selon l'une des revendications 1 à 9 ou d'une presse selon la revendication 10 pour le pressage d'une pièce pressée, en particulier pour le pressage de poudre pour obtenir une pièce en poudre pressée.
EP17181834.7A 2016-07-19 2017-07-18 Dispositif d'entraînement hydraulique Active EP3272511B1 (fr)

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DE102018120000A1 (de) * 2018-08-16 2020-02-20 Moog Gmbh Elektrohydrostatisches Aktuatorsystem mit Nachsaugbehälter
US11512716B2 (en) * 2020-01-31 2022-11-29 Bosch Rexroth Corporation Hydraulic axis with energy storage feature
DE102021121461A1 (de) 2021-08-18 2023-02-23 Dorst Technologies Gmbh & Co. Kg Pulverpresse mit hydraulischem Pressenantrieb
CN115556217B (zh) * 2022-09-22 2025-10-28 佛山市恒力泰机械有限公司 大厚度砖坯的压制成型设备及方法

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US6477835B1 (en) * 2001-08-29 2002-11-12 Moog Inc. Single-motor injection-and-screw drive hybrid actuator
US7051526B2 (en) * 2004-10-01 2006-05-30 Moog Inc. Closed-system electrohydraulic actuator
DE202007001504U1 (de) * 2007-02-01 2007-03-29 Klimas, Joachim Hydraulische Einpreßvorrichtung mit reduzierter Leistungsaufnahme
AT505724B1 (de) * 2007-09-12 2010-06-15 Trumpf Maschinen Austria Gmbh Antriebsvorrichtung für eine biegepresse
ES2622496T3 (es) * 2010-11-11 2017-07-06 Robert Bosch Gmbh Eje hidráulico
DE102011078241B3 (de) * 2011-06-28 2012-09-27 Voith Patent Gmbh Hydraulikeinheit und Verfahren zum Betreiben einer Hydraulikeinheit
DE102013020585A1 (de) * 2013-12-13 2015-06-18 Hydac Fluidtechnik Gmbh Ventilvorrichtung
DE102014226236A1 (de) * 2014-09-29 2016-03-31 Robert Bosch Gmbh Hydraulische Schaltung und Maschine mit einer hydraulischen Schaltung
DE102014219734A1 (de) * 2014-09-30 2016-03-31 Robert Bosch Gmbh Hydraulische Schaltung zur Druckmittelversorgung eines Differentialzylinders

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